WO2016014967A1 - Ensemble cadre de puissance pour pompe alternative - Google Patents

Ensemble cadre de puissance pour pompe alternative Download PDF

Info

Publication number
WO2016014967A1
WO2016014967A1 PCT/US2015/042043 US2015042043W WO2016014967A1 WO 2016014967 A1 WO2016014967 A1 WO 2016014967A1 US 2015042043 W US2015042043 W US 2015042043W WO 2016014967 A1 WO2016014967 A1 WO 2016014967A1
Authority
WO
WIPO (PCT)
Prior art keywords
segment
plate
segments
frame
frame assembly
Prior art date
Application number
PCT/US2015/042043
Other languages
English (en)
Other versions
WO2016014967A8 (fr
Inventor
Joseph H. Byrne
Chandu KUMAR
Kourosh MOMENKHANI
Jacob A. BAYYOUK
Sean P. Moran
Donald Keith PLEMONS
William Walter MARSHALL
Christopher P. BUCKLEY
Original Assignee
S.P.M. Flow Control, Inc.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=55163849&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=WO2016014967(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Priority to AU2015292399A priority Critical patent/AU2015292399B2/en
Priority to EA201790255A priority patent/EA033104B1/ru
Priority to BR112017001328-2A priority patent/BR112017001328A2/pt
Priority to EP15824524.1A priority patent/EP3194777A4/fr
Priority to EP19206779.1A priority patent/EP3660311A3/fr
Application filed by S.P.M. Flow Control, Inc. filed Critical S.P.M. Flow Control, Inc.
Priority to CN202010212158.0A priority patent/CN111502943B/zh
Priority to CN201580050937.2A priority patent/CN107076139B/zh
Priority to CA2955814A priority patent/CA2955814C/fr
Priority to MX2017000887A priority patent/MX2017000887A/es
Publication of WO2016014967A1 publication Critical patent/WO2016014967A1/fr
Publication of WO2016014967A8 publication Critical patent/WO2016014967A8/fr

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21K—MAKING FORGED OR PRESSED METAL PRODUCTS, e.g. HORSE-SHOES, RIVETS, BOLTS OR WHEELS
    • B21K23/00—Making other articles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B19/00—Machines or pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B1/00 - F04B17/00
    • F04B19/20—Other positive-displacement pumps
    • F04B19/22—Other positive-displacement pumps of reciprocating-piston type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B37/00—Pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B25/00 - F04B35/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/128—Crankcases
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/006—Crankshafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • F04B53/162—Adaptations of cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/22—Arrangements for enabling ready assembly or disassembly
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/067—Fixing them in a housing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C9/00—Bearings for crankshafts or connecting-rods; Attachment of connecting-rods
    • F16C9/02—Crankshaft bearings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21K—MAKING FORGED OR PRESSED METAL PRODUCTS, e.g. HORSE-SHOES, RIVETS, BOLTS OR WHEELS
    • B21K1/00—Making machine elements
    • B21K1/26—Making machine elements housings or supporting parts, e.g. axle housings, engine mountings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/053—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2201/00—Pump parameters
    • F04B2201/06—Valve parameters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/14—Pistons, piston-rods or piston-rod connections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B7/00—Piston machines or pumps characterised by having positively-driven valving
    • F04B7/0057—Mechanical driving means therefor, e.g. cams
    • F04B7/0069—Mechanical driving means therefor, e.g. cams for a sliding member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
    • F04B9/045—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being eccentrics
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings

Definitions

  • This disclosure relates to a reciprocating pump assembly, and in particular, a power end housing for a reciprocating pump assembly, and even more particularly, to a frame assembly for a power end housing.
  • reciprocating pumps are used for various purposes.
  • reciprocating pumps are commonly used for operations, such as cementing, acidizing, or fracing a well.
  • these reciprocating pumps are mounted to a truck, a skid or other type of platform for transport to and from the well sites.
  • such pumps deliver a fluid or slurry at pressures up to and around 20,000 psi; however, due to such extreme operating conditions, these pumps are susceptible to damage from forces caused by excessive vibrations, bending moments and/or deformation.
  • a typical reciprocating pump includes a fluid end and a power end, the power end configured to reciprocatingly move one or more plungers toward and away from a corresponding fluid end pump chamber.
  • Each chamber includes an intake port for receiving fluid, a discharge port for discharging the pressurized fluid, and a one-way flow valve in each port for preventing reverse fluid flow.
  • a plate segment for a reciprocating pump power end frame assembly having a pair of end plate segments and at least one middle plate segment disposed between the end plate segments, the plate segment consisting of the middle plate segment or one of the pair of end plate segments.
  • the plate segment includes a plate having a front wall, a rear wall, a top wall, a bottom wall and a pair of sidewalls.
  • the plate segment also includes at least one opening forming a bearing support surface, the opening extending through the plate, and at least one extension extending from at least one of the sidewalls of the plate at a position to align with and contact a corresponding extension on an adjacently positioned plate.
  • the at least one extension is integrally formed with at least one of the sidewalls of the plate.
  • the extension is a gusset extending from at least one of the sidewalls of the plate.
  • the at least one extension includes a plurality of extensions extending from at least one of the sidewalls of the plate adjacent the bearing support surface.
  • the at least one extension forms at least a portion of the front wall.
  • the at least one extension forms at least a portion of the rear wall.
  • the plate is formed of forged steel.
  • the plate includes at least one foot extending from the bottom wall to support the plate on a support surface.
  • the end plate segment includes a pair of support feet extending from the bottom wall to support the plate on a support surface.
  • the at least one extension forms at least a portion of the top wall.
  • the method includes providing a first and second frame segment, each of the frame segments having at least one extension extending from a sidewall. In some embodiments, the method also includes positioning the first frame segment adjacent the second frame segment and aligning the at least one extension of the first segment with the at least one extension of the second segment such that the at least one extension of the first segment and the at least one extension of the second segment are in contact with each other. In other embodiments, the method also includes securing the at least one extension of the first segment and the at least one extension of the second segment together to attach the first frame segment to the second frame segment.
  • the method also includes positioning the first frame segment to form a sidewall of the power end and positioning the second frame segment adjacent the first frame segment to form a middle segment of the power end.
  • the method includes forming the first and second frame segments by forging.
  • securing the at least one extension of the first segment and the at least one extension of the second segment together includes welding ends of the extensions together.
  • the method includes forming the at least one extension of at least one of the first frame segment and the second frame segment at a front wall of the respective frame segment.
  • the method includes forming the at least one extension of at least one of the first frame segment and the second frame segment at a rear wall of the respective frame segment.
  • the method includes forming the at least one extension of at least one of the first frame segment and the second frame segment at a top wall of the respective frame segment.
  • the method includes forming the at least one extension of at least one of the first frame segment and the second frame segment at a bottom wall of the respective frame segment.
  • the method includes forming an opening in each of the first and second frame segments to form a bearing support surface for supporting a bearing assembly.
  • the method includes providing a plurality of extensions around the bearing support surfaces. [0027] In another embodiment, the method includes supporting at least a portion of a crosshead tube on at least one of the plurality of extensions around the bearing support surfaces.
  • the method includes forming a recessed portion on at least a portion of the plurality of extensions to support at least a portion of a crosshead tube.
  • the power end frame for a reciprocating pump.
  • the power end frame includes a first and second end plate segment; at least one middle plate segment disposed between the first and second end plate segments; and each of the end plate segments and the at least one middle plate segment including at least one foot for supporting the power end frame assembly on a support surface.
  • the power end frame assembly includes a crosshead support member extending between the first and second end plate segments, the crosshead support member secured to each of the first and second end plate segments and the at least one middle plate segment, the crosshead support member for supporting at least a portion of at least one crosshead tube.
  • the crosshead support member includes a plurality of spaced apart recessed surfaces to support at least a portion of at least one crosshead tube.
  • the crosshead support member further includes a plurality notches sized to receive at least a portion of the first and second end plate segments and the at least one middle plate segment.
  • first and second end plate segments and the at least one middle plate segment each includes an opening extending therethrough to support a bearing assembly.
  • the at least one middle plate segment includes two spaced apart middle plate segments.
  • the at least one middle plate segment includes four middle plate segments.
  • the frame assembly includes a plurality of extensions extending between the first and second end plate segments and the at least one middle plate segment.
  • At least one of the plurality of extensions is integrally formed with an end plate segment. [0038] In still another embodiment, at least one of the plurality of extensions is integrally formed with the at least one middle plate segment.
  • the first and second end plate segments each includes a pair of support feet.
  • the frame assembly further includes an exterior skin member extending between the at least one middle plate segment and the first and second end plate segments.
  • a power end frame assembly for a reciprocating pump, the power end frame assembly including a first plate segment; a second plate segment disposed parallel to the first plate segment; and a crosshead support member secured to and extending between the first plate segment and the second plate segment, the crosshead support member configured for supporting at least a portion of a crosshead tube.
  • the at least a portion of the crosshead support member is formed integral with the first plate segment and at least another portion of the crosshead support member is formed integral with the second plate segment.
  • the crosshead support member includes a recessed portion to support at least a portion of a crosshead tube therein.
  • the crosshead support member further includes a plurality of notches sized to receive and secure to at least a portion of the first and second plate segments.
  • first and second plate segments each includes a bearing support surface forming an opening extending therethrough, the bearing support surface configured to receive and support a bearing assembly thereon.
  • the power end frame assembly includes at least two middle plate segments disposed between the first and second plate segments.
  • the crosshead support member extends between the first and second plate segments and through an opening in each of the middle plate segments.
  • FIGURE 1 is an illustration of a reciprocating pump assembly having a power end housing and a fluid end housing.
  • FIGURE 2A is a top perspective view of a frame assembly of the power end housing of FIGURE 1.
  • FIGURE 2B is a bottom perspective view of the frame assembly of FIGURE
  • FIGURE 3 is front perspective view of a middle plate segment of the frame assembly of FIGURES 2A and 2B.
  • FIGURE 4 is a partial exploded front perspective view of a plurality of the middle plate segments of FIGURE 3 having a plurality of crosshead support bars.
  • FIGURE 5 is a section view of a portion of the frame assembly of FIGURE 4 taken along the line 5— 5.
  • FIGURE 6 is a perspective view of the crosshead support bar.
  • FIGURE 7 is a front perspective view of an endplate segment of the frame assembly of FIGURES 2A and 2B.
  • FIGURE 8 is rear perspective view of a portion of the frame assembly of FIGURES 2A and 2B in which a plurality of rear support bars are secured thereto.
  • FIGURE 9 is a partial exploded front perspective view of a portion of the frame assembly of FIGURES 2A and 2B with a plurality of crosshead support tubes supported therein.
  • FIGURE 1 OA is a top perspective view of a top skin assembly.
  • FIGURE 10B is a bottom perspective view of a portion of a bottom skin assembly.
  • FIGURE IOC is a perspective view of another portion of the bottom skin assembly.
  • FIGURE 10D is a front perspective view of upper and lower nose plates.
  • FIGURE 11 is a block diagram illustrating assembly of the frame assembly of FIGURES 2A and 2B.
  • FIGURE 12 is a front perspective view of another embodiment of a frame assembly in which a plurality of forged segments having extension members extending therefrom are employed to advantage.
  • FIGURE 13 is a rear view of the frame assembly of FIGURE 12.
  • FIGURE 14 is a perspective view of an end plate segment of the frame assembly of FIGURES 12 and 13.
  • FIGURE 15 is a perspective view of a middle plate segment of the frame assembly of FIGURES 12 and 13.
  • FIGURE 16 is a perspective view of another embodiment of a middle plate segment.
  • FIGURE 17 is a perspective view of yet another embodiment of a middle plate segment.
  • FIGURES 18A and 18B are perspective views of another embodiment of left and right end plate segments.
  • FIGURE 19 is a perspective view of another embodiment of a middle plate segment.
  • FIGURE 20 is a front perspective view of two adjacently positioned middle plate segments illustrated in FIGURE 19.
  • FIGURES 21-23 are simplified section views of the frame assembly of FIGURE 29 taken along the line 21—21.
  • FIGURES 24-26 are simplified section views of a crankshaft illustrating bearing races being installed onto the crankshaft.
  • FIGURES 27 and 28 are simplified section views of the crankshaft being inserted into the frame assembly of FIGURES 40 and 41.
  • FIGURE 29 is a rear perspective view of another embodiment of a frame assembly in which the end plate segments and middle plate segments are partially cut-away.
  • FIGURES 30-38 are illustrations of the frame assembly of FIGURE 29 showing the bearing races being installed onto the bearing support surfaces.
  • FIGURE 39 is an illustration of a crankshaft support member for lifting and supporting a crankshaft during installation onto and removal from the power end housing.
  • FIGURES 40-42 are illustrations of the crankshaft support member supporting the crankshaft during installation of the crankshaft onto the power end housing.
  • FIGURE 43 is an illustration of the crankshaft support member detached from the crankshaft after installation of the crankshaft onto the power end housing.
  • FIGURES 44-47 illustrate the installation of the outer bearing assemblies to support the crankshaft on the power end housing.
  • FIGURE 48 is a front perspective view of a portion of a gearbox coupled to an end plate segment of a frame assembly.
  • FIGURE 49 is a front view of the gearbox and end plate segment of FIGURE
  • FIGURE 50 is a top view of the gearbox and end plate segment of FIGURES 48 and 49.
  • FIGURE 51 is a perspective view of an arm member illustrated in FIGURES
  • FIGURE 52 is a side view of the arm member of FIGURE 51.
  • FIGURE 53 is a section view of the arm member of FIGURE 51 taken along the line 53—53 of FIGURE 52.
  • FIGURE 54 is a section view of a portion of the frame assembly of FIGURE 48-5 taken along the line of 54— 54 of FIG. 24.
  • FIGURE 55 is a front view of a gearbox and end plate segment of FIGURE 48 illustrating an arm member secured to a trailer/skid.
  • FIGURE 56 is an illustration of the power end housing of FIGURE 1 secured to a skid.
  • FIGURE 57 is a top perspective view of the skid illustrated in FIGURE 55.
  • FIGURES 58 and 59 are illustrations of an alternate skid arrangement.
  • FIGURE 60 is a simplified illustration of the skid of FIGURES 58 and 59 secured to a trailer.
  • FIGURE 61 is an exploded cross sectional view of a portion of a middle plate segment of FIGURE 19 and a portion of the bottom skin assembly of FIGURE 10B.
  • FIGURE 62 is a cross sectional view of the bottom skin and middle plate segment of FIGURE 61 welded together.
  • FIGURE 1 is an illustration of a reciprocating pump assembly 10, such as, for example, a reciprocating plunger pump.
  • Reciprocating pumps can be used, for example, as frac pumps, mud pumps, cement pumps, and the like. Terminology may be used in this disclosure that is commonly used in a given pump system; however, unless otherwise stated, this disclosure also includes comparable components of other pump systems (e.g., crossheads and pistons).
  • the pump assembly 10 includes a power end housing 12 coupled to a fluid end housing 14 via a plurality of stay rods 20.
  • the power end housing 12 includes a crankshaft 16 depicted, for example, in FIGURE 40), which is mechanically connected to a motor (not shown), which in operation, rotates the crankshaft 16 in order to drive the reciprocating pump assembly 10.
  • rotation of the crankshaft 16 causes a plunger assembly 18 to reciprocate toward and away from the fluid end housing 14, which causes fluid to be pumped from one or more fluid cylinders (not illustrated) in the fluid end housing 14 through a discharge port 24.
  • the crankshaft 16 is cammed so that fluid is pumped from a plurality of cylinders in the fluid end housing 14 to minimize the primary, secondary and tertiary forces associated with reciprocating pumps 10.
  • the power end housing 14 employs a frame assembly 40 (FIGURES 2A and 2B), which provides for increased structural rigidity (i.e., increased resistance to deformation and/or deflection) and ease of assembly.
  • the frame assembly 40 includes a pair of end segments 42 and 44, a plurality of middle segments 46, a top skin assembly 48 and a bottom skin assembly 50 forming a forward or front wall 54, a rear or back wall 56, and a pair of sidewalls 58 and 60.
  • the frame assembly 40 includes four equally spaced apart middle segments 46 disposed between the end segments 42 and 44 to accommodate, as discussed in further detail below, five plunger assemblies 18 thereby forming a quintuplex pump assembly.
  • the frame assembly 40 is otherwise configurable.
  • the frame assembly 40 is configurable to accommodate a duplex pump assembly, which can include at least one middle segment 46 disposed between the end segments 42 and 44.
  • the frame assembly 40 is configurable to accommodate a triplex pump assembly, which includes two spaced apart middle segments 46 disposed between the end segments 42 and 44.
  • each of the segments 42, 44 and 46 are laterally spaced apart approximately twelve inches, although depending on the size of the pump assembly 10, the lateral spacing may be a longer or shorter distance. In yet other embodiments, the lateral spacing is not equal for the middle segments 46.
  • the frame assembly 40 is configured to include at least one segment 42 or 44.
  • the frame assembly 40 includes at least one segment 42 or 44 and does not include the middle segments 46.
  • the frame assembly 40 includes a plurality of feet 52, which, as discussed in greater detail below, are configured to support the power end housing 12 on a support surface, such as, for example, a skid, a truck bed, trailer or other type of platform.
  • a support surface such as, for example, a skid, a truck bed, trailer or other type of platform.
  • each end segment 42 and 44 includes a foot 52 near or adjacent to the forward wall 54 and a foot 52 near or adjacent the rear wall 56.
  • each middle segment 46 includes a foot 52 extending near or adjacent to the rear wall 56. It should be understood, however, that the number, size and position of each foot 52 is variable depending on the desired configuration.
  • an end segment 42 or 44 includes a single foot 52 extending entirely or at least partially between the front and rear walls 54 and 56.
  • one or more additional feet 52 are otherwise positionable between the feet 52 that are located near or adjacent to the front and rear walls 54 and 56.
  • an end segment 42 or 44 includes three, four or even more spaced apart feet 52 for supporting the power end housing 12.
  • the feet 52 are integrally formed on segments 42, 44 and 46; however, it should be understood that in other embodiments, the feet 52 are separately attachable to the segments 42, 44 and/or 46.
  • each middle segment 46 includes a single foot 52 generally near or adjacent to the rear wall 56.
  • each middle segment 46 includes additional feet 52.
  • a middle segment 46 includes a foot 52 (not illustrated) at or near the front wall 54 or at any other position between the front and rear wall 54 or 56 in addition to the foot 52 at or near the rear wall 56.
  • a total of eight feet 52 are used to support the power end housing 14 on a support surface (not illustrated).
  • feet 52 on the frame assembly 40 provide an increased stiffness resulting in less deflection and/or deformation of the frame assembly 40 during operation the reciprocating pump 10 thereby increasing the operating life of certain components, such as, for example, the bearings utilized to support the crankshaft 16.
  • each middle segment 46 includes upper and lower grooves 80 and 82 and a bearing support surface 84.
  • Upper and lower grooves 80 and 82 are positioned and otherwise sized so as to receive corresponding upper and lower crosshead support members 86 and 88 (FIGURE 4) that, as explained in greater detail below, provide support for crosshead support tubes 100 (FIGURE 9) and a means for more easily aligning and otherwise spacing apart the segments 42, 44 and 46.
  • upper and lower support members 86 and 88 provide structural support to the segments 42, 44 and 46, and thus, the frame assembly 40.
  • each middle segment 46 is positioned such that the upper and lower grooves 80 and 82 are aligned to receive respective portions of the upper and lower crosshead support members 86 and 88.
  • the crosshead support members 86 and 88 provide additional rigidity to and maintain alignment of the segments 42, 44 and 46 and, thus, the frame assembly 40.
  • the crosshead support members 86 and 88 are rigid rod-like members and are sized to extend through each of the middle segments 46 and attached to the end segments 42 and 44 (FIGURE 9).
  • the crosshead support members 86 and 88 are formed having a top surface 90, a bottom surface 92 and end surfaces 94 and 96.
  • the top surface 90 includes a plurality of spaced apart recessed surfaces 98, each configured to receive and otherwise support at least a portion of a crosshead tube 100 (FIGURES 2A, 2B and 9) therein.
  • the crosshead tubes 100 fit within and are supported by the recessed surfaces 98 in the upper and lower support members 86 and 88.
  • the recessed surfaces 98 are arcuately shaped and sized to receive and otherwise conform to the outer surface of the crosshead tubes 100. It should be understood, however, that the recessed surfaces 98 can be otherwise configured. For example, in some embodiments, the recessed surfaces 98 include non-arcuately formed notches or recessed areas. In other embodiments, spaced apart extension members (not illustrated) extend outward from the top surface 90 of the support members 86 and 88, the extension members being spaced apart a sufficient distance to receive and otherwise support the crosshead tube 100 therebetween to prevent movement of the crosshead tube 100 relative to the crosshead support member 86, 88.
  • each crosshead support member 86, 88 includes a support segment 102 extending between each of the recessed surfaces 98.
  • the support segments 102 are configured to facilitate alignment and attachment of the support members 86, 88 to the segments 42, 44 and 46.
  • the bottom surface 92 of the support segments 102 includes an alignment notch or recessed portion 104 positioned to receive and otherwise engage the middle segments 46.
  • the notches 104 on the upper and lower support members 86 and 88 are formed along the bottom surfaces 92 such that upon attachment of the support members 86 and 88 to the middle segments 46, such notches 104 are aligned with and are configured to conform and/or otherwise interlock with the segments 46.
  • the frame assembly 40 includes two upper crosshead support members 86 and two lower crosshead support members 88.
  • each middle segment 46 includes a pair of parallel upper grooves 80 and a pair of parallel and corresponding lower grooves 82 to accommodate a front or first pair of crosshead tube support members 106 and a rear or second pair of crosshead support members 108.
  • additional pairs of crosshead support members 86 and 88 are utilized, such as, for example, a third pair (not illustrated) of crosshead support members 86 and 88 disposed between the first and second crosshead support members 106 and 108.
  • a single pair of crosshead support member 86 and 88 is utilized. Notwithstanding the number and/or position of the crosshead support members 86 and 88, the crosshead support members 86 and 88 assist in alignment of segments 42, 44 and 46, provide additional support and structural rigidity to the frame assembly 40, both during assembly and operation of the reciprocating pump assembly 10, and provide a means to support the crosshead tubes 100 within the frame assembly 40.
  • end segment 44 is illustrated. Similar to the middle segments 46, the end segment 44 includes a bearing support surface 84 and upper and lower grooves 80 and 82 configured to receive and otherwise mate with notches 104 adjacent the end surfaces 96 on the crosshead support members 86 and 88 (FIGURE 6). While only end segment 44 is illustrated, it should be understood that end segment 42 contains a similar configuration for attachment to crosshead support members 86 and 88 at the opposite end surfaces 94.
  • the bearing support surfaces 84 form arcuately extending openings 110 extending through each of the end and middle segments 42, 44 and 46.
  • the bearing support surfaces 84 are sized to receive a bearing assembly 290 (See FIGURES 21-38 and 40-46), which facilitate the rotational movement of the crankshaft 16 (FIGURE 40).
  • the openings 1 10 formed by the bearing support surfaces 84 vary in size to facilitate the assembly of bearing assemblies 290 on respective segments 42, 44 and/or 46.
  • the rear walls 56 of the end and middle segments 42, 44 and 46 include upper and lower grooves 140 and 142.
  • an upper rod member 144 and a lower rod member 146 are disposed therein to provide additional support and rigidity to frame assembly 40.
  • two rod members 144 and 146 are illustrated.
  • a greater or fewer number of rod members 144 and 146 can be utilized.
  • the rod members 144 and 146 extend only a partial distance between the end segments 42 and 44.
  • the rod members 144 and 146 are configured in a position other than horizontally.
  • the rod members 144 and/or 146 are angularly disposed along the rear wall 56 of the frame assembly 40.
  • the rod members 144 and 146 each include spaced apart alignment notches configured to correspond to and otherwise engage with the rear wall 56 of the frame assembly 40. Such notches provide for ease of assembly and enable self-alignment of the segments 42, 44 and/or 46 during assembly.
  • the top skin assembly 48 is secured to the frame assembly 40.
  • the top skin assembly 48 includes a front plate 160 and a rear curvilinear plate 162, which together are sized to cover and otherwise enclose the top portion of the power end housing 12 between the segments 42, 44 and/or 46 by extending from the front wall 54 to the rear wall 56 of the frame assembly 40.
  • the top skin assembly 48 is a single unitary plate extending between or at least partially between the front and rear walls 54 and 56.
  • the top skin assembly 48 consists of a plurality of front and rear plates 160 and 162 that are mounted between each of the segments 42, 44 and 46 to enclose the top portion of the power end housing 12.
  • the top skin assembly 48 is formed of a single unitary sheet sized to overlay the upper or top portion of the frame assembly 40, which extends between the front wall 54, the rear wall 56 and the sidewalls 58 and 60.
  • the bottom skin assembly 50 includes a plurality of front plates 164 that are sized to fit between each of the segments 42, 44 and 46 and extending rearward from the front wall 54.
  • the bottom skin assembly 50 further includes a drain plate 166 that extends between the end segments 42 and 44, as best illustrated in FIGURE 2B.
  • the drain plate 166 further includes a plurality of drain openings 168 aligned generally beneath the middle segments 46.
  • the bottom skin assembly 50 is formed of a single unitary sheet sized to overlay the bottom portion of the frame assembly 40, which extends between the front wall 54, the rear wall 56, and the sidewalls 58 and 60.
  • FIGURE 10D illustrates upper and lower nose plates 170 and 172, which are secured to the frame assembly 40 to form at least a portion of the front wall 54, as best illustrated in FIGURE 2A.
  • an upper nose plate 170 is secured to the frame assembly 40, between segments 42, 44 and 46, above each crosshead tube 100.
  • a lower nose plate 172 is secured to the frame assembly 40, between segments 42, 44 and 46, below each crosshead tube 100.
  • the method begins at block 200 by providing at least one middle segment 46.
  • middle segments 46 For example, when assembling a quintuplex pump, four middle segments 46 are provided.
  • middle segments 46 are positioned such that the upper and lower grooves 80 and 82 on each segment 46 are aligned.
  • the crosshead support members 86 and 88 are aligned with and inserted within the upper and lower grooves 80 and 82 of each middle segment 46, as indicated at block 204.
  • the crosshead support members 86 and 88 are secured to the middle segments 46, as indicated at block 206.
  • the crosshead support members 86 and 88 are tack welded to the middle segments 46; however, any other suitable means of attachment can be used.
  • the end segments 42 and 44 are secured to the crosshead support members 80 and 82 using similar methods of attachment.
  • the method continues at block 210, where at least one rear support rod 144 or 146 is positioned along the rear wall 56 of the frame assembly.
  • a rear support rod 144 is inserted within a groove 140 disposed in each end segment 42 and 44 and each middle segment 46.
  • both an upper and lower rear support rod 144 and 146 are inserted into respective upper and lower grooves 140 and 142 on each segment 42, 44 and 46 for providing additional stability to the rear portion of the frame assembly 40.
  • the upper and lower support rods 144 and 146 are tack welded to the middle sections 46.
  • the method optionally includes securing a plurality of gussets 22 (FIGURE 2B) between each of the end segments 42, 44 and middle segments 46, which provide additional stability to the frame assembly 40.
  • the top skin assembly 48 and the bottom skin assembly 50 are secured to the frame assembly 40 by welding or other means of attachment.
  • the feet 52 on each of the segments 42, 44 and 46 are machined such that the ends of each of the feet 52 are aligned in the same plane, so that, as discussed in greater detail below, the frame assembly 40 is securable to a skid or other support surface. While FIGURE 1 1 illustrates one method for assembling the frame assembly 40, it should be understood that the method can occur in other orders.
  • the crosshead support members 86 and 88 are securable to the end segments 42 and 44 prior to securing the cross support members 86 and 88 to the middle segments 46.
  • the rear support members 140 and 142 are attachable to the segments 42, 44 and 46 prior to attaching the crosshead support members 86 and 88 to the segments 42, 44 and 46.
  • the bearing support surfaces 84 can be formed in the segments 42, 44 and/or 46 while secured to the skid.
  • each segment 44 and 46 includes gussets or extensions 650 extending from a sidewall of and formed integral with each segment 42, 44 and 46 so as to provide additional strength and stability to the frame assembly 40.
  • each segment 44 and 46 includes a plurality of extensions 650 formed integral with and extending outward from a sidewall and in spaced apart relationship around the bearing support surfaces 84.
  • each extension 650 on a middle segment 46 is positioned to align with and contact a corresponding extension 650 on an adjacently positioned end segment 42 or 44 or middle segment 46, as applicable. Additionally or alternatively, the front wall 54 of each segment 42, 44 and/or 46 is formed of an increased width such that the use and installation of separately attachable upper and lower nose plates 170 and 172 (FIGURES 2A and 2B) is not necessary.
  • the front wall 54 is formed integral with and extending from a sidewall of the segment 42, 44 and/or 46 such that when segments 42, 44 and/or 46 are adjacently positioned to form the frame assembly 40, the edges 50a and 50b of adjacently positioned frame members 42, 44 and/or 46 align and contact each other for subsequent welding and/or other forms of attachment.
  • each segment 42, 44 and/or 46 can optionally be formed with rear walls 56 integrally formed with an increased width extending from the sidewall such that the use and installation of separately attachable members disposed between each of the segments 42, 44 and/or 46 is avoided.
  • each of the segments 42, 44 and/or 46 can be formed such that, in addition to the front and rear walls 54 and 56 being formed integral with the segments 42, 44 and/or 46, the top and bottom skins 48 and 50 can be formed integral thereto, as best illustrated in FIGURE 17.
  • the edges 48a and 48b and 50a and 50b of the top and bottom skins 48 and 50, respectively, of adjacently positioned frame members 42, 44 and/or 46 contact each other for subsequent welding, thereby avoiding the need for separately attachable skins 48 and 50 to be welded between the segments 42, 44 and/or 46.
  • one or more of the segments 42, 44 and/or 46 are forged, including extensions 650; however, other methods of manufacture are available (i.e., casting or otherwise).
  • segments 42, 44 and/or 46 are forged, welding time is reduced and less machining is required. As such, this results in ease of manufacture, lower costs, and higher strength.
  • the segments 42, 44 and/or 46 are hot forged.
  • the strength of the segments 42, 44 and/or 46 is increased by about 10-15 percent from a machined segment.
  • the end segments 42 and 44 may be forged and the middle segments may be machined. In other embodiments, only one end segment 42 or 44 may be forged and all or some of the middle plate segments 46 may be forged and the remaining segments 42, 44 and/or 46 machined or otherwise formed.
  • FIGURES 18A-20 an additional embodiment of portions of the frame assembly 40 of the power end housing 12 is illustrated.
  • a plurality of extensions 650 are disposed generally adjacent to the bearing support surfaces 84 on each of the end segments 42 and 44 and the middle plate segment 46.
  • five extensions 650 are spaced apart from each other and generally around the bearing support surface 84; however, it should be understood that a greater or fewer number of extensions 650 may be utilized around the bearing support surfaces 84.
  • each plate segment 42, 44 and 46 include upper and lower extensions 652 extending outwardly therefrom and disposed generally between the front wall 54 and the bearing support surfaces 84.
  • each extension 652 is used to support the crosshead tubes 100 (FIGURE 9).
  • crosshead tube support members 86 and 88 are no longer necessary since the extensions 652 act to align and sufficiently space apart the segments 42, 44 and/or 46 while at the same time providing support to the crosshead tubes 100.
  • each extension 652 includes a curvilinear portion 654 sized to receive the cylindrical crosshead tubes 100.
  • the amount of welds can be substantially reduced (i.e., no need to weld the crosshead tube support members 86 and 88 to the frame assembly 40) because the only welding required is at the point of contact between adjacently positioned extension members 652.
  • the front wall 54 of each segment 42, 44 and/or 46 are sized and position to function in this fashion.
  • a method of assembling the frame assembly 40 illustrated in FIGURES 18A-20 is hereinafter described.
  • at least one middle segment 46 is provided.
  • four middle segments 46 are provided.
  • two middle segments 46 are provided.
  • the end segments 42 and 44 and the desired number of middle segments 46 are aligned such that the ends of each extension 650, and edges of the front walls 54, rear walls 56 and top and bottom walls 58 and 60, as applicable, are aligned and otherwise adjacent to each other for attachment by welding or otherwise.
  • the end of each extension 650 includes a planar surface having chamfered corners to facilitate welding attachment.
  • extensions 650 that are integral with segments 42, 44 and/or 46, only a single weld is necessary to connect the extensions 650 together, and thus adjacent segments 42, 44 and/or 46, rather than employing a single gusset 22 that must be welded to both adjacent segments 42, 44 and/or 46.
  • FIGURES 21-46 illustrate an embodiment of a graduated frame assembly in which the frame assembly 40 includes bearing support surfaces 84 of varying diameters to facilitate ease of installation of bearing assemblies 290 (FIGURE 28), as more fully described below.
  • FIGURE 21 which is a cross-section of the frame assembly 40 taken along the line 21— 21 of FIGURE 29
  • each bearing support surface 84 is configured to receive and otherwise support the bearing assembly 290 (FIGURE 28) to rotatably support the crankshaft 16 thereon.
  • the diameter of each of the bearing support surfaces 84 increases from the innermost middle segments 46 outward to the end segments 42 and 44.
  • the frame assembly 40 includes four middle segments 300, 302, 304 and 306 and end segments 308 and 310.
  • Each segment 300-310 includes a respective bearing support surface 312, 314, 316, 318, 320 and 322 for supporting a respective bearing assembly 290 (FIGURE 28).
  • the innermost bearing support surfaces 314 and 316 on segments 302 and 304 are formed having inner diameters smaller than the inner diameters of adjacently positioned bearing support surfaces 312 and 318 on segments 300 and 306, respectively, as represented by an amount of twice the distance Tl (FIGURE 21).
  • the bearing support surfaces 312 and 318 on segments 300 and 306, respectively are formed having diameters smaller than the inner diameters of adjacently positioned bearing support surfaces 320 and 322 on end segments 308 and 310, respectively, as represented, for example, by an amount of twice the distance of T2 (FIGURE 21).
  • the diameter of bearing support surfaces 314 and 316 is about 25 inches
  • the diameter of bearing support surfaces 312 and 318 is about 25.25 inches
  • the diameter of bearing support surfaces 320 and 322 is about 25.5 inches.
  • the diameters can vary depending on the size of the frame assembly 40.
  • the diameters can range between 2 inches to 35 inches or even larger amounts. Regardless of the size of the frame assembly 40, and as explained in greater detail below, this configuration of varying or "graduated" diameters of the bearing support surfaces 84 enables installation of the bearing assemblies 290 to be unimpeded and simplified.
  • the inner diameters of bearing support surfaces 312, 318, 320 and 322 are larger than the outer diameter of the outer bearing races 324 and 326.
  • the outer diameter of the bearing races 324 and 326 is about 25 inches.
  • the relative size differences of about 0.5 inches between the outer bearing races 324 and 326 and the diameter of bearing support surfaces 320 and 322, and the relative size differences of about 0.25 inches between the outer bearing races 324 and 326 and the diameter of bearing support surfaces 312 and 318 enable unimpeded movement of the bearing races 324 and 326 therethrough.
  • the inner diameters of at least one bearing support surface 312, 318, 320 and 322 is larger than the outer diameter of at least one of the outer bearing races 324 and 326.
  • the bearing races 324 and 326 are inserted into the frame assembly 40 in the direction of arrows 328 and 330, respectively, toward middle segments 302 and 304 and through bearing support surfaces 312, 318, 320 and 322 with adequate clearance to minimize and/or substantially reduce the likelihood of the outer bearing races 324 and/or 326 contacting the bearing support surfaces 312, 318, 320 and 322 thereby "trapping" a bearing race 324 and/or 326 in the wrong position and/or otherwise damaging the bearing races 324 or 326 and/or the bearing support surfaces 312, 318, 320 and 322.
  • the outer bearing races 324 and 326 are substantially cooled to cause the races 324 and 326 to shrink, thereby increasing the gaps between the races 324 and 326 and the support surfaces 312, 318, 320 and 322.
  • the temperature of the races 324 and 326 increases allowing the bearing races 324 and 326 to thermally expand to create an interference fit with the bearing support surfaces 314 and 316.
  • the outer bearing races 332 and 334 are then inserted into the frame assembly 40 in the direction of arrows 328 and 330, as best illustrated in FIGURES 22 and 35-38. Similar to the outer bearing races 324 and 326, the outer diameter of bearing races 332 and 334 is smaller than inner diameter of bearing support surfaces 320 and 322 to facilitate unimpeded movement of the bearing races 332 and 334 for positioning onto support surfaces 312 and 318, respectively. According to some embodiments, the outer diameter of the bearing races 332 and 334 is about 0.25 inches smaller than the inner diameters of the bearing support surfaces 320 and 322.
  • the outer diameter of the bearing races 332 and 334 may vary.
  • the outer diameter of the bearing races 332 and 334 may range between 30/1000 of an inch to 300/1000 of an inch smaller than the inner diameters of the bearing support surfaces 320 and 322.
  • the outer diameter of at least one of the bearing races 332 and 334 is equal to or smaller than 0.30 inches, 0.25 inches, 0.20 inches, 0.15 inches, or 0.10 inches smaller than the inner diameters of the bearing support surfaces 320 and 322.
  • similar variations in diameters can be seen between outer diameters of the bearing races 324 and 326 compared with the outer diameters of bearing races 332 and 334.
  • bearing races 324, 326, 332 and 334 are installed on the frame assembly 40.
  • the bearing races 324, 326, 332 and 334 are used to support the crankshaft 16 on the frame assembly 40, as illustrated, for example, in FIGURE 28 and 41.
  • the crankshaft 16 includes a plurality of journals 400, 402, 404, 406, 408 and 410 that are configured to receive a plurality of bearing races 412 and 414 thereon.
  • journals 404 and 406 are formed having a diameter that is larger than the diameters of journals 402 and 408.
  • journals 402 and 408 are formed having a diameter that is larger than the diameter of journals 400 and 410.
  • the diameters of journals 402 and 408 are between about 0.030 and 0.062 inches smaller than the diameter of the journals 404 and 406, although it should be understood that the relative lengths may be either larger or smaller.
  • the diameter of the journals 400 and 410 are between about 0.062 and 0.124 inches smaller than the diameter of the journals 404 and 406, although it should be understood that the relative lengths may be either larger or smaller. Regardless of the diameter size of journals 400, 402, 404, 406, 408 and 410, the varying sized diameters provide ease of installation and/or removal of crankshaft bearings from the crankshaft 16.
  • the inner bearing races 412 are first installed followed by the inner bearing races 414.
  • an inner diameter of the inner bearing races 412 is larger than the outer diameters of journal surfaces 400, 402, 408 and 410, which facilitates unimpeded installation of the bearing races 412 onto the crankshaft 16, and in particular, journals 404 and 406.
  • the inner bearing races 412 are positioned adjacent to each end of the crankshaft 16 and moved in the direction of arrows 328 and 330 toward journals 404 and 406.
  • a pair of inner bearing races 414 are then positioned onto journals 402 and 408, as illustrated in FIGURE 26.
  • the inner diameter of the inner bearing races 414 is larger than the diameter of journals 400 and 410 to facilitate unimpeded movement in the direction of arrows 328 and 330 across the journals 400 and 410.
  • the outer bearing components which include bearing races 416 and 418, are then installed onto and around the journals 400 and 410, as best illustrated in FIGURE 26.
  • the crankshaft 16 in addition to sizing the components to have different non-interfering diameters, the crankshaft 16 is optionally cooled to a predetermined temperature in order to effectuate thermal cooling thereby causing the crankshaft to contract in size.
  • the inner bearing races 412, 414, 416 and 418 are positionable on the crankshaft 16.
  • the bearing races 412, 414, 416 and 418 are secured to the crankshaft 16 by an interference fit.
  • inner bearing races 412, 414, 416 and 418 can be heated (e.g., such as by induction heating) to a predetermined temperature thereby causing the inner bearing races 412, 414, 416 and 418 to increase in size. Inner bearings races 412, 414, 416 and 418 can then be positioned on crankshaft 16 and secured thereto by an interference fit.
  • crankshaft 16 is secured inside the frame assembly 40.
  • the crankshaft 16 is moved in the direction of arrow 328 such that the inner bearing races 412 are aligned with and otherwise engage outer bearing races 324 and 326, the inner bearing races 414 are aligned with and otherwise engage the outer bearing races 332 and 334, and the bearing race 418 is aligned with the opening 110 on the end segment 44.
  • the crankshaft 16 can be installed on the opposite side of the frame assembly 40 such that when moved in the direction opposite of arrow 328, the crankshaft 16 is inserted within the frame assembly 40.
  • crankshaft support device 700 is employed for supporting the crankshaft 16 during installation and removal thereof.
  • the crankshaft support device 700 is configured to support the crankshaft 16 in a generally horizontal position as illustrated, for example, in FIGURE 40, so as to facilitate alignment of the crankshaft 16 with the bearing support surfaces 84.
  • the crankshaft 16 is movable along a horizontal axis (lifted and supported via a crane or otherwise) in the direction of arrow 328 for insertion within the openings 110 formed by the bearing support surfaces 84.
  • the support device 700 is detached from the crankshaft 16.
  • the support device 700 includes a frame assembly 702 having a first segment 704 oriented to extend substantially along the length of the crankshaft 16 and a second portion 706 extending from the first portion 704.
  • the frame assembly further includes a base section 708, which as described in further detail below, is used to secure the crankshaft 16 to the support device 700.
  • the second portion 706 extends a predetermined distance from the first portion 704 so as to enable the crankshaft 16 to be spaced apart from the first portion 704 such that when inserting the crankshaft inside the bearing support surfaces 84, the first portion 704 does not contact any portion of the power end housing 12.
  • the base section 708 includes a cavity 710 sized to correspond to and receive an end of the crankshaft 16 therein.
  • the crankshaft end includes threaded openings corresponding to openings 716 in the base section 708.
  • the openings 716 are aligned with corresponding openings in the end of the crankshaft 16 and a pair of threaded screws 718 are inserted therethrough to securely fasten the crankshaft 16 to the support device 700.
  • the first section 704 includes a pair of eyelets 720 for receiving and engaging with a hanging structure, such as a chain 722, that extends from a crane or other lifting structure (not illustrated).
  • the eyelets 720 are positioned on the first section 704 and the length of the chains 722 are sized so that the crankshaft 16, when secured to the support device 700, remains generally horizontal and/or otherwise parallel with an axis extending through the center of the openings 1 10 formed by the bearing support surfaces 84.
  • the eyelets 720 have lifting shackles (not illustrated) inserted therein to secure the support device 700 to the chains.
  • One lifting shackle attaches to a single length chain and the second shackle attaches to an adjustable chain to provide tiling freedom during installation.
  • the eyelet 720 that is farthest from second portion 706 can be engaged with an adjustable hanging structure, such as chain 722, such that crankshaft 16 can be balanced substantially horizontally (e.g., to facilitate alignment of the crankshaft 16 with the bearing support surfaces 84) by adjusting the adjustable hanging structure.
  • support structure 700 may be otherwise configured.
  • the first section 704 may extend a distance longer or shorter than the overall length of the crankshaft 16.
  • the length of the second section 706 may otherwise vary (i.e., may be longer or shorter than that depicted in FIGURES 39-43) and may extend in any direction other than perpendicularly from the first section 704.
  • the support structure 700 is formed of metal, wherein the first section 704, the second section 706 and the base section are welded together. It should be understood however, that the support structure 700 may be otherwise formed from a non- metallic material and be, for example, a single contiguous structure formed without welding.
  • crankshaft 16 is installed in the power end 12
  • a pair of carrier members 420 and 422, which support bearing races 290 thereon, are installed onto the end segments 310 and 308, respectively, for supporting the crankshaft 16 for rotatable movement thereof.
  • a gearbox 600 is secured to the end plate 44 of the frame assembly 40 via a pair arm members 602 to resist movement of the gearbox 600 relative to the frame assembly 40.
  • two arm members 602 are illustrated; however, in other embodiments, a greater or fewer number of arm members 602 may be employed.
  • three or more arm members 602 are secured between the end plate 44 and the gearbox 600 to resist relative movement between the end plate 44 and the gearbox 600.
  • the position of the arm members 602 are optimized in order to resist rotational and axial movement to prevent and/or otherwise eliminate damage to the frame 40 and/or gearbox 600, including the outer housing and thus, the components therein.
  • the first and second ends 604 and 606 of the arm members 602 are secured to the end plate of gearbox 600 (e.g., at gusset 620) and end plate 44 of frame assembly 40 (e.g., at gusset 620),, respectively, such that the arm members 602 extend in a parallel configuration and in the same plane (FIGURE 50).
  • the arm members 602 In the embodiment illustrated in FIGURE 48, the arm members 602 generally extend and are otherwise disposed in a vertical plane that is near and/or otherwise adjacent to the front wall 54 of the frame assembly 40.
  • the arm members 602 may be otherwise configured to accommodate a different size and/or center of gravity of the gearbox 600, which varies depending on the size of the reciprocating pump assembly 10.
  • the arm members 602 may be secured in a non-parallel fashion and/or extend in different planes.
  • the arm members 602 instead of being positioned and secured near or adjacent to the front wall 54 of the frame assembly 40, may be secured at other positions, such as, for example, at any position between the front wall 54 and the rear wall 56 of the frame assembly 40.
  • the arm members 602 are secured at any position along the gearbox 600 to resist rotational and/or axial movement of the gearbox 600 relative to the frame assembly 40.
  • the arm member 602 includes an elongate body 608 and ball joints 610 at the first and second ends 604 and 606 to facilitate pivotable movement, as discussed further below, during installation of and attachment of the arm members 602 to the gearbox 600 and the frame assembly 40. Furthermore, in some embodiments, each arm member 602 is adjustable in length to accommodate different sized configurations of the reciprocating pump assembly 10.
  • each ball joint 610 is movable relative to the elongate body 608 via a pair of threaded adjustment bolts 612, such that, when it is desired to extend the length of the arm member 602, the elongate body 608 is rotated relative to the bolts 612 on each end 604 and 606.
  • the body member 608 is rotated in the direction of arrow 614 (FIGURE 51), which in turn causes rotational movement of the body member 608 with respect to the bolts 612 (FIGURE 53) to extend the length of the arm member 602.
  • the body member 602 is rotated in the direction opposite of arrow 614 to cause movement of the body member 608 with respect to the bolts 612 to reduce the length of the arm member 602.
  • a pair of nuts 616 are tightened so that they abut against the body 608 to prevent relative movement of the adjustment bolts 612 relative to the elongate body 608.
  • the arm member 602 may be otherwise configured.
  • the arm member 602 is of a fixed length without the ability to be adjusted in length.
  • the arm member 602 includes only one end 604 or 606 that is adjustable in length.
  • the arm member 602 includes only a single threaded bolt 612 being adjustable to lengthen or shorten the arm member 602.
  • the arm member 602 includes telescoping portions (not illustrated) that slide and otherwise move in a telescoping relationship to adjust the length thereof.
  • a cotter pin or any other locking device is usable to secure the telescoping segments to prevent separation and/or relative movement between the members during operation of the pump assembly 10.
  • the arm members 602 are secured to the pump assembly 10 and the gearbox 600 via a shoulder bolt 618 disposed in each end 604 and 606.
  • the shoulder bolts 618 secure the ends of the support members 602 to respective gussets 620 on the power end housing 12 and the gearbox 600 (FIGURE 49).
  • each shoulder bolt 618 is sized to fit within a corresponding counterbore 622 formed in each gusset 620.
  • each counterbore includes a first section 622a having a first diameter and a second section 622b having a second diameter.
  • the first diameter is larger than the second diameter so as to, as discussed in further detail below, receive corresponding portions of the shoulder bolt 618 therein to reduce failure of the shoulder bolt 618, which oftentimes occurs in response to shear stresses generated during operation of the reciprocating pump assembly 10.
  • the shoulder bolt 618 includes a first portion 618a having a first diameter and a second portion 618b having a second diameter, the diameters of the first and second portions 618a and 618b corresponding to the diameters of portions 622a and 622b of the counterbore 622.
  • the shoulder bolt 618 is secured within the counterbore 622 via a threaded connection between portions 618b and 622b of the shoulder bolt 618 and the counterbore 622, respectively.
  • the first portion 622a of the counterbore 622 is precision machined to have a clearance between the first portion 618a of the shoulder bolt 618 and the first portion 622a of the counterbore 622 of about 0.002 inches.
  • first portion 618a of the shoulder bolt 618 may vary (i.e., the clearance therebetween may be greater or less than 0.002 inches).
  • first section 618a larger than the second section 618b the shear stresses acting on the threaded section 618b are reduced thereby reducing the likelihood of failure of the connection between the arm member 602 and the frame assembly 40 and the gearbox 600.
  • the gearbox 600 is secured to the power end housing 12. Once secured, at least one arm member 602 is provided for attachment between the end segment 44 and the gearbox 600 to resist relative movement, including relative axial and rotational movement, between the gearbox 600 and the power end housing 12.
  • the length of the arm member 602 is first adjusted to the necessary length so as to connect to both the power end housing 12 and the gearbox 600. Once positioned to the desired length, the ends 604 and 606 of the arm member 602 are aligned with the counterbores 622 on the respective power end housing 12 and the gearbox 600.
  • the shoulder bolts 618 are then inserted through ball joints 610 on respective ends 604 and 606 and then into the counterbores 622. Each shoulder bolt 618 is tightened within the counterbores 622 to prevent separation of the shoulder bolts 618 from the counterbores 622.
  • either end 604 or 606 is first secured to either the power end housing 12 or the gearbox 600 as previously described. Once secured thereto, the unsecured or free end 604 or 606 is pivoted via the ball joint 610 so that the ball joint 610 on the unsecured end of the arm member 602 is otherwise aligned with the counterbore 622 on the power end housing 12 or the gearbox 600, whichever is unattached to the arm member 602. Once aligned, a shoulder bolt 618 is used to secure the second end 604 or 606 to the corresponding counterbore 622.
  • the length of the arm member 602 is adjusted, as previously discussed, so that the ball joint 610 aligns with the counterbore 622 to enable the shoulder bolt 618 to secure the arm member 602 thereto.
  • the arm members 602 are secured between the gearbox 600 and the power end housing 12, the arm members 602 may be otherwise utilized.
  • one arm member 602 is secured between the power end housing 12 and a second arm 602 is secured between the gearbox 600 and either a skid or a trailer 660.
  • the arm members 602 may both extend from the gearbox 600 and the power end housing 12 directly to the skid and/or trailer 660.
  • the skid 500 includes a base member 502, the base member having a pair of side segments 504 and 506, transverse segments 508, 510, and 512 extending between and connecting the side segments 504 and 506, and feet 514 for supporting the skid 500 on a support surface.
  • the skid 500 includes a plurality of pads 516, 518, 520, 522, 524, 526, 528 and 530 that correspond to feet 52 on the frame assembly 40.
  • pads 520, 522, 524 and 526 correspond to and are positioned to align with the feet 52 on the middle segments 46.
  • pads 516, 518, 528 and 530 correspond to and are positioned to align with feet 52 on the end segments 42 and 44.
  • the skid 500 further includes a pair of pads 532 and 534 to support at least a portion of the fluid end housing 14 (FIGURE 1).
  • the side segments 504, 506 and transverse segment 508 each include a plurality of gussets 540 secured thereto to increase the stiffness of the skid 500 to resist bending and torsional loading.
  • each side segment 504 and 506 include two spaced apart gussets 540 and the transverse segment 508 includes five spaced apart gussets 540, disposed between the pads 518, 520, 522, 524, 526, and 530. It should be understood, however, that a greater or fewer number of gussets 540 may be utilized on the skid 500 to increase the stiffness thereof.
  • the pads 520, 522, 524 and 526 have a thickness that is different from the thickness of pads 516, 518, 528 and 530.
  • the pads 520, 522, 524 and 526 have a thickness that is less than the thickness of pads 516, 518, 528 and 530.
  • the varying thickness provides a gap between the feet 52 and the pads 520, 522, 524 and 526 to enable the frame assembly 40 to be shimmed in order to reduce "rocking", vibration, deformation and other unwanted movement.
  • the feet 52 on segments 42, 44 and 46 are machined so as to lie on the same plane such that when frame assembly is supported on the pads 516, 518, 520, 522, 524, 526, 528 and 530, feet 52 on end segments 42 and 44 are in contact with pads 516, 518, 528 and 530 and feet 52 on middle segments 46 are aligned with but otherwise spaced apart from pads 520, 522, 524 and 526 to provide a gap to receive a shim or other spacer element.
  • the desired shim or other spacer elements can be inserted in the gaps formed between the feet 52 and the pads 520, 522, 524 and 526 to reduce and or otherwise eliminate rocking or other unwanted movement of the power end housing 12 relative to the skid 500.
  • the feet 52 on middle segments 46 are formed to extend onto a different plane than the plane containing the feet 52 on the end segments 42 and 44 and the pads 520, 522, 524 and 526 have a lesser thickness than the pads 516, 518, 528 and 530.
  • each pad 516-528 is the same thickness and shims are used to fill any gap between the foot 52 and the pads 516-528.
  • the pads have a differing thickness to accommodate bends in the skid 500.
  • the pads 518, 520, 522, 524, 526, and/or 530 are machined, as needed, such that a top surface of the pads 518', 520', 522', 524, 526', and/or 530' rest in the same plane.
  • the thickness of pad 530 will be greater than the thickness of the pad 518, because a greater portion of the pad 518 must be removed in order for surfaces 518' and 530' to lie in the same plane.
  • the skid 800 includes transverse support members 808, 810 and 812 extending between and connecting the side segments 804 and 806.
  • the transverse support members 810 and 812 are formed having a hollow interior and provide additional rigidity and support for the areas around the pads 816, 828, 832 and 834.
  • the transverse segment 808 is shaped as an I-beam and includes a plurality of vertical gussets 840 disposed on each side of a web member 841; however, it should be understood that the transverse segment may be shapes other than an I-beam shape.
  • the skid 800 further includes a plurality of vertical gussets 840 disposed on the side segments 804 and 806.
  • the side segments 804 and 806 are formed having a "C" shaped channel in which the gussets 840 are disposed therein; however, it should be understood that the side segments 804 and 806 can be formed other than "C” shaped.
  • the side segments 804 and 806 each include a plurality angularly disposed gussets 842 disposed within the "C" shaped channel. Gussets 840 and 842 provide additional support and rigidity to the skid 800.
  • the transverse segment 508 includes a plurality of gussets 840 disposed around pads 818, 820, 822, 824, 826 and 830 and on both sides of the web 841 to provide additional support when the power end housing 12 is secured to the skid 800.
  • the gussets 840 are positioned so as to form a channel 844 to provide access to mounting bolts (not illustrated) to enable tighten mounting bolts to secure the feet 52 to the skid 800.
  • each side segment 804 and 806 optionally includes a reinforcing plate 862 secured thereto to provide additional rigidity to the skid 800.
  • the reinforcing plate 862 extends substantially between the transverse support members 808 and 810. Although the reinforcing plates may extend for lesser distances and/or be formed of multiple sections.
  • skids 500 and 800 may be otherwise configured. For example, a greater or fewer number of transverse segments may be utilized. Likewise, additional side segments may be positioned parallel to side segments 504, 506 and 804, 806. In other embodiments, additional segments may be angularly disposed between the side segments, the transverse segments or any combinations thereof.
  • the skid 800 further includes a plurality mounting openings 846 disposed on the side segments 804 and 806, the openings 846 spaced apart and positioned to enable the skid 800 to be secured to a trailer 848 (FIGURE 60).
  • the trailer 848 includes a chassis 850 having longitudinal frame segments 852 and 854 and a transverse segment 856 extending between the longitudinal frame segments 852 and 854.
  • the longitudinal segments 852 and 854 include slots positioned to align with the slots 846 on the skid 800 to enable the skid 800 to be secured to the chassis 850 via a plurality of bolts or any other suitable attachment means.
  • the slots 846 are elongated so as to accommodate differing sized chassis 850 (i.e., the longitudinal frame segments 852 and 854 being spaced farther apart or closer together).
  • a bracket 860 is optionally attachable to and cantilevers from the chassis 850 so as to provide additional support to the skid 800 when the power end housing 12 is secured thereto.
  • the bottom skin 164 is welded to the middle plate segment 46.
  • the bottom skin 164 is formed having a generally "J" shaped groove 920 on each edge to be joined with the corresponding segment 46 (or end plate segment 42 or 44, as applicable) at its weld joint edge near the outer surface.
  • the segment 46 has a generally reverse "J" shaped groove 905 and a backing step 910.
  • the backing step 910 supports the root surface 919 of the bottom skin 164 on a backing surface 915.
  • the backing surface 915 transitions to the "J" groove 905 with a mating surface 913, which abuts the mating end 917 of the bottom skin 164.
  • the mating surface 913 prevents lateral movement of the bottom skin 164.
  • mating surface 913 has a depth about 0.06 inches and the backing surface 915 is extended for about 0.13 inches from the mating surface 913.
  • the mating end 917 is about 0.06 inches thick and can thus evenly join the "J" groove 920 with the "J" groove 905, as further described below.
  • the "J" groove 920 of the bottom skin 164 is joined with the "J" groove 905 of the segment 46 to form a "U” groove for receiving weld metal to enable formation of a complete penetration weld, without requiring a separate a backing plate.
  • a molten weld metal 930 is provided to the "U" groove formed from the two "J" grooves 905 and 920.
  • the weld metal 930 may be the same or materially similar to the base metal of the segment 46 and the bottom skin 164.
  • welding fusion occurs between the weld metal 930, the bottom skin 164 and the segment 46 and forms a fused region 935 though the thickness of the segment 46, thus unifying the three pieces (i.e., the segment 46, the weld material 930, and the bottom skin 164) into one.
  • the fused region may have a thickness of about 0.06" to 0.13", depending on welding power and material.
  • the solidified weld metal 930 may not necessarily be planed as illustrated but a proximate plane surface can be achieved with proper control of the amount of the weld metal 930.
  • Various welding methods may be used, such as flux-cored arc welding, gas metal arc welding, submerged arc welding, or other appropriate method.
  • the segment 46, the weld metal 930, and the bottom skin 164 may be submerged in a solution for welding.
  • the various embodiments and aspects described herein provide multiple advantages such as, for example, providing a power end housing frame assembly 40 having components that can self-align, enable bearing assemblies to be inserted with minimal risk that the bearing assemblies will be trapped on the bearing support surfaces, can be more easily assembled, require less welding, can be manufactured at a reduced weight, and have increased strength thereby operating with less deflection and/or deformation to increase the operating life and integrity of the frame assembly 40 while at the same time reducing manufacturing costs.
  • specific terminology has been resorted to for the sake of clarity.

Abstract

L'invention concerne un segment de plaque pour un ensemble cadre d'extrémité de puissance pour pompe alternative, l'ensemble cadre d'extrémité de puissance ayant une paire de segments de plaque d'extrémité et au moins un segment de plaque intermédiaire disposé entre les segments de plaque d'extrémité. Le segment de plaque est constitué du segment de plaque intermédiaire ou d'un segment de la paire de segments de plaque d'extrémité et comprend une plaque ayant une paroi avant, une paroi arrière, une paroi supérieure, une paroi inférieure et une paire de parois latérales et au moins une ouverture formant une surface de support de palier, l'ouverture s'étendant à travers la plaque. Le segment de plaque comprend en outre au moins une extension s'étendant depuis au moins une des parois latérales de la plaque dans une position pour s'aligner et venir en contact avec une extension correspondante sur une plaque positionnée de manière adjacente.
PCT/US2015/042043 2014-07-25 2015-07-24 Ensemble cadre de puissance pour pompe alternative WO2016014967A1 (fr)

Priority Applications (9)

Application Number Priority Date Filing Date Title
MX2017000887A MX2017000887A (es) 2014-07-25 2015-07-24 Montaje estructural del extremo de energia para bomba de movimiento alternante.
EA201790255A EA033104B1 (ru) 2014-07-25 2015-07-24 Рама в сборе, предназначенная для приводной части возвратно-поступательного насоса
BR112017001328-2A BR112017001328A2 (pt) 2014-07-25 2015-07-24 segmento de placa, método para montagem de uma extremidade de potência, e, conjunto de armação de extremidade de potência
EP15824524.1A EP3194777A4 (fr) 2014-07-25 2015-07-24 Ensemble cadre de puissance pour pompe alternative
EP19206779.1A EP3660311A3 (fr) 2014-07-25 2015-07-24 Ensemble cadre de puissance pour pompe alternative
AU2015292399A AU2015292399B2 (en) 2014-07-25 2015-07-24 Power frame assembly for reciprocating pump
CN202010212158.0A CN111502943B (zh) 2014-07-25 2015-07-24 用于往复泵的动力端框架组件
CN201580050937.2A CN107076139B (zh) 2014-07-25 2015-07-24 用于往复泵的动力端框架组件
CA2955814A CA2955814C (fr) 2014-07-25 2015-07-24 Ensemble cadre de puissance pour pompe alternative

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
US201462029271P 2014-07-25 2014-07-25
US62/029,271 2014-07-25
US201462095689P 2014-12-22 2014-12-22
US62/095,689 2014-12-22
US201562155793P 2015-05-01 2015-05-01
US62/155,793 2015-05-01

Publications (2)

Publication Number Publication Date
WO2016014967A1 true WO2016014967A1 (fr) 2016-01-28
WO2016014967A8 WO2016014967A8 (fr) 2017-03-02

Family

ID=55163849

Family Applications (4)

Application Number Title Priority Date Filing Date
PCT/US2015/042104 WO2016015006A1 (fr) 2014-07-25 2015-07-24 Support de pompe alternative
PCT/US2015/042111 WO2016015012A1 (fr) 2014-07-25 2015-07-24 Système et procédé de renforcement de pompe alternative
PCT/US2015/042043 WO2016014967A1 (fr) 2014-07-25 2015-07-24 Ensemble cadre de puissance pour pompe alternative
PCT/US2015/042078 WO2016014988A1 (fr) 2014-07-25 2015-07-24 Système de palier pour pompe à mouvement alternatif et procédé d'assemblage

Family Applications Before (2)

Application Number Title Priority Date Filing Date
PCT/US2015/042104 WO2016015006A1 (fr) 2014-07-25 2015-07-24 Support de pompe alternative
PCT/US2015/042111 WO2016015012A1 (fr) 2014-07-25 2015-07-24 Système et procédé de renforcement de pompe alternative

Family Applications After (1)

Application Number Title Priority Date Filing Date
PCT/US2015/042078 WO2016014988A1 (fr) 2014-07-25 2015-07-24 Système de palier pour pompe à mouvement alternatif et procédé d'assemblage

Country Status (9)

Country Link
US (9) US9879659B2 (fr)
EP (5) EP3660311A3 (fr)
CN (6) CN110360074A (fr)
AU (5) AU2015292354B2 (fr)
BR (4) BR112017001351A2 (fr)
CA (6) CA3031128C (fr)
EA (4) EA034261B1 (fr)
MX (6) MX2017000887A (fr)
WO (4) WO2016015006A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
USD791193S1 (en) 2015-07-24 2017-07-04 S.P.M. Flow Control, Inc. Power end frame segment
USD791192S1 (en) 2014-07-25 2017-07-04 S.P.M. Flow Control, Inc. Power end frame segment
US9695812B2 (en) 2013-03-15 2017-07-04 S.P.M. Flow Control, Inc. Reciprocating pump assembly
US10316832B2 (en) 2014-06-27 2019-06-11 S.P.M. Flow Control, Inc. Pump drivetrain damper system and control systems and methods for same
US10352321B2 (en) 2014-12-22 2019-07-16 S.P.M. Flow Control, Inc. Reciprocating pump with dual circuit power end lubrication system
US10436766B1 (en) 2015-10-12 2019-10-08 S.P.M. Flow Control, Inc. Monitoring lubricant in hydraulic fracturing pump system

Families Citing this family (39)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9822894B2 (en) 2013-11-26 2017-11-21 S.P.M. Flow Control, Inc. Valve seats for use in fracturing pumps
US11480170B2 (en) * 2014-07-25 2022-10-25 Spm Oil & Gas Inc. Support for reciprocating pump
US11209124B2 (en) * 2016-06-23 2021-12-28 Spm Oil & Gas Inc. Power frame and lubrication system for a reciprocating pump assembly
EP3267034B1 (fr) * 2016-07-07 2020-05-13 Cameron Technologies Limited Ensemble de pompe à boue à auto-alignement
AR111523A1 (es) 2017-03-14 2019-07-24 Gardner Denver Petroleum Pumps Llc Placa de desgaste para una bomba de perforación
US10781803B2 (en) * 2017-11-07 2020-09-22 S.P.M. Flow Control, Inc. Reciprocating pump
CN109869294A (zh) * 2019-04-19 2019-06-11 烟台杰瑞石油装备技术有限公司 一种超大功率五缸柱塞泵
US11578710B2 (en) 2019-05-02 2023-02-14 Kerr Machine Co. Fracturing pump with in-line fluid end
US11773843B2 (en) * 2019-06-07 2023-10-03 Schlumberger Technology Corporation Integral reciprocating pump structure supporting spacer section
US11773844B2 (en) 2019-06-07 2023-10-03 Schlumberger Technology Corporation Reciprocating pump trunnions connecting crosshead and connecting rod
WO2021081750A1 (fr) * 2019-10-29 2021-05-06 烟台杰瑞石油装备技术有限公司 Pompe à piston plongeur à cinq cylindres de support à points multiples
US11009024B1 (en) * 2019-11-11 2021-05-18 St9 Gas And Oil, Llc Power end for hydraulic fracturing pump
US20220397107A1 (en) 2019-11-18 2022-12-15 Kerr Machine Co. Fluid end assembly
US11686296B2 (en) 2019-11-18 2023-06-27 Kerr Machine Co. Fluid routing plug
US11578711B2 (en) 2019-11-18 2023-02-14 Kerr Machine Co. Fluid routing plug
US11644018B2 (en) 2019-11-18 2023-05-09 Kerr Machine Co. Fluid end
US11635068B2 (en) * 2019-11-18 2023-04-25 Kerr Machine Co. Modular power end
WO2021102036A1 (fr) 2019-11-18 2021-05-27 Kerr Machine Co. Pompe haute pression
US20210207589A1 (en) * 2020-01-07 2021-07-08 Moien Ibrahim Louzon Fracturing pump assembly
US11353117B1 (en) 2020-01-17 2022-06-07 Vulcan Industrial Holdings, LLC Valve seat insert system and method
WO2021178335A1 (fr) * 2020-03-02 2021-09-10 S.P.M. Flow Control, Inc. Soupape de pompe assistée par actionnement
CA3187352A1 (fr) * 2020-06-15 2021-12-23 Schlumberger Canada Limited Systemes et procede de douille de crosse de piston
US11421680B1 (en) 2020-06-30 2022-08-23 Vulcan Industrial Holdings, LLC Packing bore wear sleeve retainer system
US11421679B1 (en) 2020-06-30 2022-08-23 Vulcan Industrial Holdings, LLC Packing assembly with threaded sleeve for interaction with an installation tool
US11384756B1 (en) 2020-08-19 2022-07-12 Vulcan Industrial Holdings, LLC Composite valve seat system and method
USD980876S1 (en) 2020-08-21 2023-03-14 Vulcan Industrial Holdings, LLC Fluid end for a pumping system
USD986928S1 (en) 2020-08-21 2023-05-23 Vulcan Industrial Holdings, LLC Fluid end for a pumping system
USD997992S1 (en) 2020-08-21 2023-09-05 Vulcan Industrial Holdings, LLC Fluid end for a pumping system
US20220220952A1 (en) * 2021-01-08 2022-07-14 Moien Ibrahim Louzon Fracturing pump assembly
US11391374B1 (en) 2021-01-14 2022-07-19 Vulcan Industrial Holdings, LLC Dual ring stuffing box
US11920583B2 (en) 2021-03-05 2024-03-05 Kerr Machine Co. Fluid end with clamped retention
USD1025158S1 (en) * 2021-04-13 2024-04-30 360 Gearboxes & Diffs Pty Ltd Bearing retainer plate
US11946465B2 (en) 2021-08-14 2024-04-02 Kerr Machine Co. Packing seal assembly
CN114738261B (zh) * 2021-11-10 2023-07-07 烟台杰瑞石油装备技术有限公司 一种柱塞泵用的变径曲轴和动力端壳体及其装配方法
US11808364B2 (en) 2021-11-11 2023-11-07 Kerr Machine Co. Valve body
US11434900B1 (en) 2022-04-25 2022-09-06 Vulcan Industrial Holdings, LLC Spring controlling valve
US11953000B2 (en) 2022-04-25 2024-04-09 Kerr Machine Co. Linear drive assembly
US11920684B1 (en) 2022-05-17 2024-03-05 Vulcan Industrial Holdings, LLC Mechanically or hybrid mounted valve seat
CN115013281B (zh) * 2022-08-04 2022-11-08 宁波合力机泵股份有限公司 一种以泵机身为基准的双支承大功率往复泵及其组装工艺

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2056622A (en) * 1933-04-04 1936-10-06 Sulzer Ag Multicylinder reciprocating piston machine
US4477237A (en) * 1982-05-10 1984-10-16 Grable William A Fabricated reciprocating piston pump
US20080078583A1 (en) * 2006-09-28 2008-04-03 Milburn Eugene Cummins Method for assembling a modular fluid end for duplex pumps
US20100129249A1 (en) * 2007-05-17 2010-05-27 Dresser Italia S.R.L. Frame for fluid machines
EP2397694A1 (fr) * 2010-06-21 2011-12-21 Fives Cryomec AG Unité d'entraînement pour une pompe alternative

Family Cites Families (318)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA27491A (fr) 1887-08-24 Edward E. Thorpe Sachet
US2899247A (en) 1959-08-11 Feed water pump
US364627A (en) 1887-06-14 Steam-engine
US879560A (en) 1905-10-05 1908-02-18 Daniel F Lepley Triplex pump.
CA153846A (fr) 1913-03-15 1914-02-17 William Roberts Auvent
US1356036A (en) 1919-05-08 1920-10-19 George A Buckley Combined plow and scraper
US1418202A (en) 1921-05-20 1922-05-30 Ingersoll Rand Co Vertical compressor unit
GB204454A (en) 1922-07-29 1923-10-04 Joseph Streda A device for facilitating the screwing together of lengths of piping
US1490294A (en) * 1922-08-29 1924-04-15 Nickolas A Steffen Engine
US1596037A (en) * 1923-10-03 1926-08-17 Delco Light Co Pumping apparatus
US1707228A (en) 1924-09-18 1929-04-02 Clyde A Knapp Srosshead
US1890428A (en) 1928-05-23 1932-12-06 Oilgear Co Pump rig
US1899743A (en) 1928-12-13 1933-02-28 Gen Motors Res Corp Slide valve engine
GB361192A (en) * 1930-02-05 1931-11-19 Marius Jean Baptiste Barbarou Improvements in internal combustion engines
US1893699A (en) * 1930-08-26 1933-01-10 Reliance Electric & Eng Co Method of mounting units
US1901358A (en) * 1931-01-24 1933-03-14 Pratt & Whitney Aircraft Compa Crank shaft
US1867585A (en) 1931-02-16 1932-07-19 Thomas F Moore Vacuum pump
US1926925A (en) 1931-04-07 1933-09-12 Gulf Res & Dev Corp Pin, bolt, and other connecting device
US1981995A (en) * 1933-12-04 1934-11-27 Municipal Appliance Company Frame assembly for mounting a unitary device on an automobile chassis
US2249802A (en) 1939-03-20 1941-07-22 Wilson John Hart Slush pump
US2461056A (en) 1943-03-29 1949-02-08 American Steel Foundries Connecting rod and plunger connection
US2428602A (en) 1944-01-12 1947-10-07 Frank B Yingling Connecting rod assembly
US2420779A (en) 1944-04-10 1947-05-20 Carl L Holmes Opposed piston engine
US2443332A (en) 1944-04-14 1948-06-15 Hpm Dev Corp Seal
US2682433A (en) * 1949-02-02 1954-06-29 United States Steel Corp Crosshead assembly
US2561227A (en) 1949-06-01 1951-07-17 Wade R Reed Triple capacity plunger pump
US2665555A (en) 1949-07-15 1954-01-12 Gunnar R C Martinsson Hydraulic mechanism
US2729117A (en) 1950-10-03 1956-01-03 Maybach Motorenbau Gmbh Multicrank driving mechanism for internal-combustion engines
DE975401C (de) 1952-04-01 1961-11-23 Gutehoffnungshuette Sterkrade Kolbenstangenverbindung
US2766701A (en) 1953-03-09 1956-10-16 Nat Supply Co Plunger and cylinder for pump
US2755739A (en) 1953-07-20 1956-07-24 Lever Brothers Ltd Proportioning pump
US2878990A (en) 1953-10-30 1959-03-24 Sulzer Ag Upright piston compressor
US2823085A (en) 1954-02-06 1958-02-11 Kloeckner Humboldt Deutz Ag Piston for internal combustion engines
US2828931A (en) 1954-05-21 1958-04-01 Harvey Machine Co Inc Skid for handling machinery
US3163474A (en) 1956-06-06 1964-12-29 Wilson Mfg Co Inc Mud pumps
US2991003A (en) 1957-01-30 1961-07-04 Robert S Petersen Piston and compressor structure
US3158211A (en) 1957-09-16 1964-11-24 Leyman Corp Well drilling apparatus
US2883874A (en) 1958-02-03 1959-04-28 Halliburton Oil Well Cementing Heavy duty pump
US3049082A (en) 1958-05-26 1962-08-14 John W Mecom Reciprocating pump
US3053195A (en) * 1959-04-14 1962-09-11 Larkin R Williamson High pressure hydraulic pump
US3238892A (en) 1960-02-01 1966-03-08 Kobe Inc High speed triplex pump
US3039317A (en) 1960-07-21 1962-06-19 Hough Co Frank Disconnect means for a pump drive
DE1191069B (de) 1960-09-29 1965-04-15 Borsig Ag Hochdruckkolbenkompressor
US3137179A (en) 1960-12-16 1964-06-16 M C M Machine Works Piston rod and piston assembly
US3236315A (en) 1961-12-21 1966-02-22 Salem Tool Co Auger mining machine
US3168665A (en) 1962-01-02 1965-02-02 Molon Motor & Coil Corp Multiple rotor induction motor unit
US3179451A (en) 1962-11-01 1965-04-20 Ingersoll Rand Co Wrist pin assembly
DE1455657A1 (de) 1963-02-14 1969-02-13 Opel Adam Ag Biegesteif ausgebildetes Antriebsaggregat,insbesondere fuer Kraftfahrzeuge
US3206242A (en) 1964-01-22 1965-09-14 Herbert L Fensin Split-ring hoisting clamp
US3358352A (en) 1964-07-20 1967-12-19 Luther H Wilcox Axle bearing puller
US3356036A (en) 1966-03-01 1967-12-05 Fred J Repp Plunger-type pump
US3493201A (en) 1967-03-15 1970-02-03 Nash Engineering Co Universal support base for pumps,compressors or the like
GB1236395A (en) 1967-08-16 1971-06-23 Ricardo & Co Engineers Lubrication of bearings of reciprocating engines
US3487892A (en) 1968-05-31 1970-01-06 William J Kiefer Positive displacement lubrication system
US3583052A (en) * 1969-03-11 1971-06-08 Trw Inc Method of manufacture and use of staked turnbuckle assembly
US3595101A (en) 1969-07-11 1971-07-27 Gaso Pump And Burner Mfg Co Reciprocating pump having improved crankshaft bearing arrangement
US3596101A (en) 1969-11-05 1971-07-27 Canon Kk Optical systems for automatic focusing apparatus
DE2053987A1 (de) 1970-11-03 1972-05-10 Pumpenfabrik Urach, 7417 Urach Mehrzylinder Kurbelwellen Maschine, insbesondere Kolbenpumpe oder kompressor
US3757149A (en) 1972-02-16 1973-09-04 Molon Motor & Coil Corp Shading coil motor assembly
US4048909A (en) 1972-11-01 1977-09-20 Air Products And Chemicals, Inc. Piston ring
US3880604A (en) 1974-01-14 1975-04-29 Wallace H Hawkins Press for removing bearings
US3883941A (en) 1974-05-01 1975-05-20 Frederick J Coil Universal-type, pillow-block bearing puller
US4129974A (en) 1974-06-18 1978-12-19 Morris Ojalvo Warp-restraining device and improvement to beams, girders, arch ribs, columns and struts
CH588885A5 (fr) 1974-08-21 1977-06-15 Sulzer Ag
US3967542A (en) 1974-11-20 1976-07-06 Kelsey-Hayes Company Hydraulic intensifier
US4013057A (en) 1975-05-14 1977-03-22 Dana Corporation Piston assembly
US4210399A (en) 1975-08-04 1980-07-01 Atul Jain System for relative motion detection between wave transmitter-receiver and irregular reflecting surface
SE404764B (sv) 1976-04-28 1978-10-30 Volvo Penta Ab Vevstake samt forfarande och gjutform for framstellning av vevstaken
US4099447A (en) * 1976-09-20 1978-07-11 Ada Pumps, Inc. Hydraulically operated oil well pump jack
JPS5944049B2 (ja) 1976-10-19 1984-10-26 株式会社豊田中央研究所 脳圧計
US4140442A (en) 1977-03-14 1979-02-20 Perfect Pump Co., Inc. High pressure pump
FR2385938A1 (fr) 1977-03-30 1978-10-27 Fives Cail Babcock Dispositif de lubrification pour paliers a patins supportant une piece tournante de grand diametre, telle qu'un broyeur rotatif
US4211190A (en) 1978-02-27 1980-07-08 Robert Indech Groove guided piston linkage for an internal combustion engine
US4341508A (en) 1979-05-31 1982-07-27 The Ellis Williams Company Pump and engine assembly
US4269569A (en) 1979-06-18 1981-05-26 Hoover Francis W Automatic pump sequencing and flow rate modulating control system
US4338054A (en) 1979-11-19 1982-07-06 Dahl Norman C Solid externally threaded fasteners having greatly increased ductility
US4381179A (en) 1980-10-31 1983-04-26 Lear Siegler, Inc. Pumps with floating wrist pins
US5076220A (en) 1980-12-02 1991-12-31 Hugh G. Evans Internal combustion engine
GB2106433B (en) 1981-09-22 1985-11-06 Ae Plc Squeeze casting of pistons
US4512694A (en) 1982-02-01 1985-04-23 Associated Dynamics, Incorporated Method and apparatus for alignment of gearing
US4494415A (en) 1982-03-25 1985-01-22 Hydra-Rig, Incorporated Liquid nitrogen pump
US4553298A (en) 1982-05-10 1985-11-19 Grable William A Method for fabricating a reciprocating piston pump
US4388837A (en) 1982-06-28 1983-06-21 Bender Emil A Positive engagement fail safe mechanism and lift belt construction for long stroke, well pumping unit
US4476772A (en) 1982-11-04 1984-10-16 Corbett Elevator Manufacturing Co., Inc. Caging seal for hydraulic elevator or the like
JPS60175753A (ja) 1984-02-20 1985-09-09 Ngk Insulators Ltd セラミツクス組み込み型ピストン
JPS60180969A (ja) 1984-02-28 1985-09-14 日本碍子株式会社 エンジン部品およびその製造法
US4606709A (en) 1984-07-20 1986-08-19 Special Projects Mfg. Co. Liquid pump with sequential operating fluid pistons
DE3441508A1 (de) 1984-11-14 1986-05-22 Klöckner-Humboldt-Deutz AG, 5000 Köln Einrichtung zum verstellen des einspritzzeitpunktes oder der ventilsteuerzeiten einer brennkraftmaschine
FR2573136B1 (fr) 1984-11-15 1989-03-31 Schlumberger Cie Dowell Procede d'observation des caracteristiques de pompage sur une pompe a deplacement positif et pompe permettant de mettre en oeuvre ce procede.
JPS61135961A (ja) 1984-12-05 1986-06-23 Ngk Insulators Ltd セラミツクス製ピストンヘツド付きピストン
US4638971A (en) * 1986-02-04 1987-01-27 Dowell Schlumberger Incorporated Machinery skid
GB8606998D0 (en) 1986-03-20 1986-04-23 Ae Plc Pistons
US4762051A (en) 1986-07-17 1988-08-09 Dresser Industries, Inc. Single acting pump with double acting drive
US4729249A (en) * 1986-08-25 1988-03-08 Dresser Industries, Inc. Reciprocating plunger pump having separate and individually removable crosshead cradles
US5063775A (en) 1987-08-19 1991-11-12 Walker Sr Frank J Method and system for controlling a mechanical pump to monitor and optimize both reservoir and equipment performance
US4803964A (en) 1986-12-11 1989-02-14 Wladyslaw Kurek Internal combustion engine
US4771801A (en) 1987-02-02 1988-09-20 Halliburton Services Protective cover assembly with reverse buckling disc
BR8700642A (pt) 1987-02-09 1988-08-30 Metal Leve Sa Embolo articulado
FR2611826B1 (fr) * 1987-02-25 1989-06-16 Masseron Alain Bras telescopique pouvant etre concu sous forme demontable
US4809646A (en) 1987-03-18 1989-03-07 Paul Marius A High pressure reciprocator components
GB8714287D0 (en) 1987-06-18 1987-07-22 Ae Plc Pistons
FR2618509B1 (fr) 1987-07-22 1991-09-06 Citroen Messian Durand Engren Reducteur a arbres paralleles ou orthogonaux a couple divise et rattrapage de jeux
JPH0194453A (ja) 1987-10-06 1989-04-13 Nec Corp トレース収集出力方式
JPH01194453A (ja) 1988-01-29 1989-08-04 Fujitsu Ltd 半導体装置
US4824342A (en) 1988-02-16 1989-04-25 Hypro Corp. Chemical injector system for piston pumps
US4842039A (en) 1988-06-27 1989-06-27 Otto Kelm Self-aligning plunger tip
US4966109A (en) 1989-04-05 1990-10-30 Hitachi Construction Machinery Co., Ltd. Hydraulic connecting rod
IT1229654B (it) 1989-04-21 1991-09-06 Nuovo Pignone Spa Testa a croce perfezionata per macchine alternative a stantuffo, in particolare per compressori alternativi.
US5159743A (en) 1989-05-08 1992-11-03 Posi Lock Puller, Inc. Hydraulic puller
US5313061A (en) 1989-06-06 1994-05-17 Viking Instrument Miniaturized mass spectrometer system
US4950145A (en) 1989-06-15 1990-08-21 Anthony-Thomas Candy Company Apparatus for molding chocolate
US5033177A (en) 1989-09-08 1991-07-23 Innovative Tools & Equipment Corporation Sleeve bearing puller and installer
US5135031A (en) 1989-09-25 1992-08-04 Vickers, Incorporated Power transmission
US5060603A (en) 1990-01-12 1991-10-29 Williams Kenneth A Internal combustion engine crankdisc and method of making same
US5115725A (en) 1990-03-30 1992-05-26 Isuzu Motors Limited Piston and connecting rod assembly
EP0449278B1 (fr) 1990-03-30 1994-12-07 Isuzu Motors Limited Structure de connexion d'un piston et d'une tige
JP2920004B2 (ja) 1990-07-23 1999-07-19 日本碍子株式会社 セラミックスと金属の鋳ぐるみ複合体
US5156534A (en) 1990-09-04 1992-10-20 United Technologies Corporation Rotary machine having back to back turbines
US5080319A (en) 1990-09-24 1992-01-14 Erka Corporation Adjustable position mounting device and method
DE4108786C2 (de) 1991-03-18 1995-01-05 Hydromatik Gmbh Leichtkolben für hydrostatische Axial- und Radialkolbenmaschinen
US5062311A (en) * 1991-03-29 1991-11-05 Dresser-Rand Company Frame, crankshaft and crosshead assembly, and a crankshaft and crosshead frame, for a reciprocating-piston machine
US5078580A (en) 1991-03-29 1992-01-07 Dresser-Rand Company Plural-stage gas compressor
RU2037700C1 (ru) 1991-05-05 1995-06-19 Савеловское Производственное Объединение "Прогресс" Кинематическая передача
US5165160A (en) 1991-07-22 1992-11-24 Poncelet George V Apparatus and method for axially aligning straight or curved conduits
US5249600A (en) 1991-12-31 1993-10-05 Blume George H Valve seat for use with pumps for handling abrasive fluids
US5247873A (en) 1992-01-28 1993-09-28 Cooper Industries, Inc. Connecting rod assembly with a crosshead
US5287612A (en) 1992-02-27 1994-02-22 Goulds Pumps, Incorporated Apparatus for removal of a bearing frame assembly
CN2120103U (zh) * 1992-02-28 1992-10-28 北京市崇文区环境卫生管理局 一种用于起重垃圾集装箱的吊钩装置
US5337612A (en) 1992-06-08 1994-08-16 Quartzdyne, Inc. Apparatus for pressure transducer isolation
US5246355A (en) 1992-07-10 1993-09-21 Special Projects Manufacturing, Inc. Well service pumping assembly
JPH08503757A (ja) 1992-08-10 1996-04-23 ダウ、ドイチュラント、インコーポレーテッド． 圧縮機を監視し制御するための方法及び装置
AU7323994A (en) 1993-07-13 1995-02-13 Sims Deltec, Inc. Medical pump and method of programming
US5370093A (en) 1993-07-21 1994-12-06 Hayes; William A. Connecting rod for high stress applications and method of manufacture
JP3026410B2 (ja) 1993-08-28 2000-03-27 南 昌煕 往復動機器のピストン
BR9304034A (pt) 1993-10-19 1995-06-20 Brasil Compressores Sa Biela bi-partida para compressor hermético alternativo
US5425306A (en) 1993-11-23 1995-06-20 Dana Corporation Composite insert for use in a piston
JPH07208479A (ja) 1994-01-28 1995-08-11 Mitsubishi Heavy Ind Ltd 内燃機関の軸受装置
DE4416120A1 (de) 1994-05-06 1995-11-09 Mahle Gmbh Zweiteiliger Kolben
US5846056A (en) 1995-04-07 1998-12-08 Dhindsa; Jasbir S. Reciprocating pump system and method for operating same
US6446682B1 (en) 1995-06-06 2002-09-10 James P. Viken Auto-loading fluid exchanger and method of use
US5673666A (en) 1995-10-17 1997-10-07 General Motors Corporation Connecting rod for internal combustion engine
US5772403A (en) 1996-03-27 1998-06-30 Butterworth Jetting Systems, Inc. Programmable pump monitoring and shutdown system
US5682851A (en) 1996-11-14 1997-11-04 Caterpillar Inc. Oil system for an engine that includes an auxiliary priming pump
DE19653164C2 (de) 1996-12-19 2000-03-23 Brueninghaus Hydromatik Gmbh Verfahren zur Herstellung eines Pumpenkolbens
US5820092A (en) * 1997-02-28 1998-10-13 Thaler; Ken Modular assembly kit for constructing roof mounted support structures
US5839888A (en) 1997-03-18 1998-11-24 Geological Equipment Corp. Well service pump systems having offset wrist pins
US5855397A (en) 1997-04-02 1999-01-05 Cummins Engine Company, Inc. High-pressure sealable connector for a pressure sensor
JPH10288086A (ja) 1997-04-10 1998-10-27 Yamaha Motor Co Ltd 内燃機関用ピストン
KR100275877B1 (ko) 1997-12-29 2000-12-15 구자홍 밀폐형 압축기의 커넥팅 로드 조립구조
US6260004B1 (en) 1997-12-31 2001-07-10 Innovation Management Group, Inc. Method and apparatus for diagnosing a pump system
KR19990060438A (ko) 1997-12-31 1999-07-26 구자홍 밀폐형 압축기의 커넥팅로드 오일공급구조
JPH11200947A (ja) 1998-01-14 1999-07-27 Toyota Motor Corp 内燃機関用ピストン
KR19990079544A (ko) 1998-04-07 1999-11-05 카오루 수에요시 플런저펌프 및 그 시스템
US5984645A (en) 1998-04-08 1999-11-16 General Motors Corporation Compressor with combined pressure sensor and high pressure relief valve assembly
GB2342421B (en) 1998-10-08 2003-03-19 Mmd Design & Consult A Conveyor
KR100287572B1 (ko) 1998-11-09 2001-06-01 조영호 용매이송펌프및그구동방법
KR100302886B1 (ko) 1998-11-20 2001-11-22 이종진 왕복압축기
US6183212B1 (en) 1999-02-17 2001-02-06 Stanadyne Automotive Corp. Snap-in connection for pumping plunger sliding shoes
FI105848B (fi) 1999-03-26 2000-10-13 Valmet Corp Menetelmä paperikoneen tai vastaavan telahydrauliikan painejärjestelmässä ja telahydrauliikan monipainejärjestelmä
US6873267B1 (en) 1999-09-29 2005-03-29 Weatherford/Lamb, Inc. Methods and apparatus for monitoring and controlling oil and gas production wells from a remote location
US6557457B1 (en) 1999-12-01 2003-05-06 Federal-Mogul World Wide, Inc. Bushingless piston and connecting rod assembly and method of manufacture
KR20010065249A (ko) 1999-12-29 2001-07-11 구자홍 밀폐형 압축기의 커넥팅로드 설치구조 및 그 방법
US7374005B2 (en) 2000-01-10 2008-05-20 The United States Of America As Represented By The Administrator Of The U.S. Environmental Protection Agency Opposing pump/motors
CN2436688Y (zh) 2000-05-15 2001-06-27 台州市椒江永乐喷雾器厂 柱塞泵泵体
US6611078B1 (en) 2000-07-19 2003-08-26 Tri-Seven Research, Inc. Flux diode motor
US6405992B1 (en) 2000-09-19 2002-06-18 Kermit L. Palmer Pregrouted baseplate for supporting rotating machinery
US6419459B1 (en) 2000-10-02 2002-07-16 Gardner Denver, Inc. Pump fluid cylinder mounting assembly
US7374905B2 (en) 2000-11-08 2008-05-20 Oxyrase, Inc. Medium composition, method and device for selectively enhancing the isolation of anaerobic microorganisms contained in a mixed sample with facultative microorganisms
US6663349B1 (en) 2001-03-02 2003-12-16 Reliance Electric Technologies, Llc System and method for controlling pump cavitation and blockage
DE10129046B4 (de) 2001-06-15 2006-01-05 Ks Kolbenschmidt Gmbh Kolben für eine Brennkraftmaschine mit einem Eingußkörper
JP2002371905A (ja) 2001-06-18 2002-12-26 Denso Corp 内燃機関の制御装置、内燃機関の慣性モーメント推定方法、内燃機関の負荷推定方法および内燃機関の運転制御方法
US20030024386A1 (en) 2001-08-02 2003-02-06 Burke Walter T. Resilient element for a piston head
KR100426085B1 (ko) 2001-10-25 2004-04-06 삼성광주전자 주식회사 밀폐형 왕복동식 압축기의 커넥팅로드 장치
WO2003038320A1 (fr) 2001-11-01 2003-05-08 Per Olav Haughom Procede et dispositif place au niveau d'un piston de pompe hydrodynamique
JP3974386B2 (ja) 2001-11-19 2007-09-12 ヤマハモーターエレクトロニクス株式会社 電動駆動装置の減速ギヤ機構
DE20120609U1 (de) 2001-12-20 2002-03-21 Festo Ag & Co Diagnoseeinrichtung für eine fluidtechnische Einrichtung sowie damit ausgestattete fluidtechnische Einrichtung
US20030118104A1 (en) 2001-12-21 2003-06-26 Intel Corporation System, method, and software for estimation of motion vectors
US6697741B2 (en) 2002-01-31 2004-02-24 Honda Giken Kogyo Kabushiki Kaisha Method and system for evaluating and monitoring hydraulic pump noise levels
US6581261B1 (en) 2002-06-10 2003-06-24 Yu-Lin Chen Large size clamping device for detaching bearing
USD496670S1 (en) 2002-09-24 2004-09-28 Maruyama Mfg. Co., Inc. Reciprocating pump
USD495342S1 (en) 2002-09-24 2004-08-31 Maruyama Mfg. Co., Inc. Reciprocating pump
US6859740B2 (en) 2002-12-12 2005-02-22 Halliburton Energy Services, Inc. Method and system for detecting cavitation in a pump
US6882960B2 (en) 2003-02-21 2005-04-19 J. Davis Miller System and method for power pump performance monitoring and analysis
CN2612816Y (zh) 2003-03-30 2004-04-21 泰安市水利机械厂 高压柱塞泥浆泵
US20040213677A1 (en) 2003-04-24 2004-10-28 Matzner Mark D. Monitoring system for reciprocating pumps
US6718955B1 (en) 2003-04-25 2004-04-13 Thomas Geoffrey Knight Electric supercharger
US20040219040A1 (en) 2003-04-30 2004-11-04 Vladimir Kugelev Direct drive reciprocating pump
US7404704B2 (en) 2003-04-30 2008-07-29 S.P.M. Flow Control, Inc. Manifold assembly for reciprocating pump
DE10322194A1 (de) 2003-05-16 2004-12-09 Siemens Ag Diagnosesystem und -verfahren für ein Ventil, insbesondere ein Rückschlagventil einer Verdrängerpumpe
US7219594B2 (en) 2003-06-06 2007-05-22 S.P.M. Flow Control, Inc. Coolant system for piston and liner of reciprocating pumps
DE10332872A1 (de) 2003-07-19 2005-02-17 Braun Gmbh Handzahnbürste
GB0319552D0 (en) 2003-08-20 2003-09-24 Reactec Ltd Improvments in or relating to vibration contol
US7044216B2 (en) 2003-11-05 2006-05-16 Grant Prideco, L.P. Large diameter flush-joint pipe handling system
KR100440555B1 (ko) 2003-12-10 2004-07-15 주식회사 현대특수강 강관의 시공방법
CN2758526Y (zh) 2003-12-24 2006-02-15 沈阳气体压缩机股份有限公司 十字头液压联接紧固装置
CN2674183Y (zh) 2003-12-24 2005-01-26 沈阳气体压缩机股份有限公司 十字头液压联接紧固装置及活塞杆弹性杆结构
JP4347682B2 (ja) 2003-12-25 2009-10-21 株式会社ソミック石川 ボールジョイントおよびそのベアリングシート
US7220119B1 (en) 2004-02-28 2007-05-22 Force Pro Pre-stressed tie rod and method of manufacture
CN2705626Y (zh) 2004-03-12 2005-06-22 中国石化集团江汉石油管理局第四机械厂 五缸泥浆泵
US7385984B2 (en) * 2004-03-30 2008-06-10 Extreme Networks, Inc. Packet processing system architecture and method
US7364412B2 (en) 2004-08-06 2008-04-29 S.P.M. Flow Control, Inc. System, method, and apparatus for valve stop assembly in a reciprocating pump
JP2006097491A (ja) 2004-09-28 2006-04-13 Aisin Seiki Co Ltd エンジンのオイル供給装置
SE527767C2 (sv) 2004-10-22 2006-05-30 Volvo Lastvagnar Ab Fästelement
GB2419671A (en) 2004-10-29 2006-05-03 Spm Flow Control Inc Pressure monitoring system for a reciprocating pump
US8186900B2 (en) 2005-02-16 2012-05-29 National-Oilwell, L.P. Piston rod retention system
US20100160710A1 (en) 2005-03-11 2010-06-24 Strickland Michael L Methods and apparatuses for reducing emissions of volatile organic compounds from pumps and storage tanks for voc-containing fluids
GB0506803D0 (en) * 2005-04-04 2005-05-11 Cummins Power Generation Ltd Support stands for power plants
GB0508447D0 (en) 2005-04-26 2005-06-01 Disenco Ltd Displacer piston assembly
US7425120B2 (en) 2005-04-26 2008-09-16 Wanner Engineering, Inc. Diaphragm position control for hydraulically driven pumps
JP4511431B2 (ja) 2005-08-01 2010-07-28 株式会社丸山製作所 往復ポンプ装置
CA2511254C (fr) 2005-08-04 2007-04-24 Westport Research Inc. Compresseur de gaz haute pression et methode d'utilisation
US7111604B1 (en) 2005-08-15 2006-09-26 Fev Motorentechnik Gmbh Connecting rod for an internal combustion engine
US7811064B2 (en) 2005-08-18 2010-10-12 Serva Corporation Variable displacement reciprocating pump
JP2007051615A (ja) 2005-08-19 2007-03-01 Anest Iwata Corp 往復ピストン式気体圧縮機
US20070099746A1 (en) 2005-10-31 2007-05-03 Gardner Denver, Inc. Self aligning gear set
USD538824S1 (en) 2005-11-30 2007-03-20 Maruyama Mfg. Co., Inc. Reciprocating pump
US7552903B2 (en) 2005-12-13 2009-06-30 Solar Turbines Incorporated Machine mounting system
CN2900853Y (zh) 2006-05-18 2007-05-16 四机赛瓦石油钻采设备有限公司 大排量柱塞泵
US7610847B2 (en) 2006-06-27 2009-11-03 Fmc Technologies, Inc. Pump crosshead and connecting rod assembly
CN2926584Y (zh) 2006-06-28 2007-07-25 成都奥科得动力配件制造有限公司 三缸泥浆泵十字头
US8672606B2 (en) * 2006-06-30 2014-03-18 Solar Turbines Inc. Gas turbine engine and system for servicing a gas turbine engine
CN200961570Y (zh) * 2006-09-24 2007-10-17 中国石化集团江汉石油管理局第四机械厂 五缸泵泵壳
JP2008095831A (ja) 2006-10-12 2008-04-24 Toyota Motor Corp 内燃機関の複合コネクティングロッド
CN200964929Y (zh) 2006-10-24 2007-10-24 烟台杰瑞石油装备技术有限公司 一种带有蜗轮蜗杆减速器的油井作业用三缸柱塞泵
CN100394025C (zh) 2007-01-23 2008-06-11 西安交通大学 一种往复式压缩机的高压级润滑方法
US7665974B2 (en) 2007-05-02 2010-02-23 Wanner Engineering, Inc. Diaphragm pump position control with offset valve axis
DE102007028446B4 (de) * 2007-06-18 2022-11-24 Sew-Eurodrive Gmbh & Co Kg Fundamentrahmen oder Motorschwinge für eine Getriebe-Motor-Einheit und Verfahren
CN201092955Y (zh) 2007-09-04 2008-07-30 上海宝钢设备检修有限公司 容积泵曲轴尾端轴承装置
US8100048B2 (en) 2007-10-02 2012-01-24 Federal-Mogul Corporation Pinless piston and connecting rod assembly
US8083504B2 (en) 2007-10-05 2011-12-27 Weatherford/Lamb, Inc. Quintuplex mud pump
US7931078B2 (en) 2008-02-22 2011-04-26 Scope Production Developments Ltd. Stuffing box apparatus
DE102008010567A1 (de) * 2008-02-22 2009-08-27 Esmo Ag Maschinengestell, Maschine
US7653975B2 (en) 2008-03-21 2010-02-02 Chih Kuo Hu Clamping apparatus of a puller
USD591311S1 (en) * 2008-05-20 2009-04-28 Maruyama Mfg. Co., Inc. Reciprocating pump
CN102119311B (zh) * 2008-08-11 2014-03-26 开利公司 单元安装的驱动器与制冷机振动的隔离
US7753131B2 (en) 2008-08-20 2010-07-13 Tam International, Inc. High temperature packer and method
DE102008058521B4 (de) * 2008-11-21 2012-05-16 Sew-Eurodrive Gmbh & Co. Kg Baureihe von Antriebspaketen und Verfahren
US8162631B2 (en) 2008-11-25 2012-04-24 S.P.M. Flow Control, Inc. Floating pinion bearing for a reciprocating pump
US20100158726A1 (en) 2008-12-19 2010-06-24 Dixie Iron Works, Ltd. Plunger Pump
US8376723B2 (en) 2009-01-08 2013-02-19 Weir Spm, Inc. Connecting rod without wrist pin
US20100260631A1 (en) 2009-01-08 2010-10-14 Weir Spm, Inc. Multi-piece connecting rod
CN101476558A (zh) 2009-01-22 2009-07-08 四川石油管理局成都天然气压缩机厂 柔性活塞杆
JP5044580B2 (ja) 2009-01-29 2012-10-10 株式会社小松製作所 作業車両の油圧システム
US20100242720A1 (en) 2009-03-27 2010-09-30 Weir Spm, Inc. Bimetallic Crosshead
US20100322802A1 (en) 2009-06-23 2010-12-23 Weir Spm, Inc. Readily Removable Pump Crosshead
US8601687B2 (en) 2009-08-13 2013-12-10 Schlumberger Technology Corporation Pump body
US9188123B2 (en) 2009-08-13 2015-11-17 Schlumberger Technology Corporation Pump assembly
WO2011027273A2 (fr) 2009-09-03 2011-03-10 Schlumberger Canada Limited Corps de pompe
CN201610828U (zh) 2009-12-08 2010-10-20 焦阳 一种超高压柱塞清洗泵及其柱塞组件的自动调心结构
US8701546B2 (en) 2009-12-15 2014-04-22 Gardner Denver Water Jetting Systems, Inc. Coupling arrangement providing an axial space between a plunger and plunger adaptor of a high pressure fluid pump
WO2013071286A1 (fr) 2011-11-10 2013-05-16 J-Mac Tool, Inc. Système de pompe
US9341179B2 (en) 2010-02-26 2016-05-17 Schlumberger Technology Corporation Precompression effect in pump body
US8857374B1 (en) 2011-05-13 2014-10-14 Classic Brands, LLC Hopper type wild bird feeder
CA2737321C (fr) * 2010-05-18 2013-09-17 Gerald Lesko Pompe a boue
JP5775575B2 (ja) 2010-06-24 2015-09-09 グラコ ミネソタ インコーポレーテッド モータ位置を調整可能なデュアルポンプ式流体混合装置
DE102010027214B4 (de) 2010-07-15 2013-09-05 Continental Automotive Gmbh Verfahren und Steuergerät zum Steuern einer Brennkraftmaschine
US9335090B2 (en) 2010-07-22 2016-05-10 Red Bull Gmbh Refrigerator
DE102010034086A1 (de) 2010-08-12 2012-02-16 Marco Systemanalyse Und Entwicklung Gmbh Hochdruckpumpe
USD668266S1 (en) * 2010-09-17 2012-10-02 Molon Motor And Coil Corporation Peristaltic pump front housing
FR2965199B1 (fr) 2010-09-24 2012-09-07 Serimax Bride d'aide au travail de tubes comportant plusieurs parties.
US8376432B1 (en) 2010-10-04 2013-02-19 Hagler Systems, Inc. Impeller jig
CN201836038U (zh) 2010-10-26 2011-05-18 中国有色(沈阳)泵业有限公司 一种隔膜泵的十字头与活塞杆的连接装置
US8529230B1 (en) 2010-10-26 2013-09-10 Black Horse, Llc Retaining mechanisms for threaded bodies in reciprocating pumps
CN201874803U (zh) 2010-11-23 2011-06-22 宝鸡石油机械有限责任公司 用于连接钻井泵中间拉杆和活塞杆的装置
US20120141305A1 (en) 2010-12-02 2012-06-07 Landers R Scott Stay Rod for a High Pressure Oil Field Pump
UA109683C2 (uk) 2010-12-09 2015-09-25 Зміщений клапанний отвір у поршневому насосі
USD658684S1 (en) 2010-12-27 2012-05-01 Whirlpool S.A. Compressor frame
US20120167759A1 (en) 2010-12-29 2012-07-05 Spm Flow Control, Inc. Short Length Pump Having Brine Resistant Seal and Rotating Wrist Pin and Related Methods
DE102011009592A1 (de) * 2011-01-27 2012-08-02 Liebherr-Werk Biberach Gmbh Fundamentverankerung für Arbeitsmaschine
CN201961961U (zh) * 2011-02-10 2011-09-07 中国石油天然气股份有限公司 高压柱塞泵曲轴吊装工具
USD671276S1 (en) 2011-03-14 2012-11-20 Bryan Krueger Bird feeder
USD708401S1 (en) 2011-03-14 2014-07-01 Classic Brands, LLC Fill component of a bird feeder
USD678911S1 (en) 2011-04-20 2013-03-26 Clemon Prevost Water pump adapter
US10024310B2 (en) * 2011-04-28 2018-07-17 Afglobal Corporation Modular pump design
CN202186832U (zh) 2011-08-03 2012-04-11 天津第一机床总厂 加工圆形工件的吊装工具
EP2557306A1 (fr) * 2011-08-08 2013-02-13 Delphi Technologies Holding S.à.r.l. Pompe à carburant
CN202279641U (zh) * 2011-08-18 2012-06-20 安徽白兔湖汽配有限公司 一种曲轴小吊车
DE102011081483A1 (de) 2011-08-24 2013-02-28 Mahle International Gmbh Verfahren zur vereinfachten und lagegenauen Fixierung eines Nockenwellenmoduls an einem Zylinderkopf
CN102371537A (zh) 2011-10-12 2012-03-14 潘旭华 一种曲轴连杆颈随动磨削用的曲轴夹持方法
WO2013067134A1 (fr) * 2011-11-01 2013-05-10 Cummins Power Generation, Inc. Plate-forme modulaire
US20130112074A1 (en) * 2011-11-03 2013-05-09 FTS International, LLC Support Mechanism for the Fluid End of a High Pressure Pump
USD670312S1 (en) 2011-11-29 2012-11-06 Fna Ip Holdings, Inc. Pump
US20130145591A1 (en) 2011-12-13 2013-06-13 Yu-Lin Chen Pressing disc for disassembling bearings
CN104204519B (zh) 2012-02-01 2016-08-03 S.P.M.流量控制股份有限公司 具有集成腹板部分的泵流体端
EP2626525A1 (fr) 2012-02-13 2013-08-14 Wärtsilä Schweiz AG Grand moteur doté d'un dispositif de lubrification de cylindre et procédé de lubrification d'un cylindre d'un grand moteur
CN202527901U (zh) * 2012-03-01 2012-11-14 中国石油天然气股份有限公司 高压往复泵曲轴拆卸专用工具
USD678628S1 (en) 2012-03-28 2013-03-19 Classic Brands, LLC Nectar bottle for a bird feeder
CN202493418U (zh) 2012-03-30 2012-10-17 四川宏华石油设备有限公司 钻井泵底座
US8833301B2 (en) 2012-04-02 2014-09-16 Classic Brands, LLC Bird feeder with rotating perch
USD700622S1 (en) 2012-04-19 2014-03-04 Don V. Carruth Plunger adapter
NL2008949C2 (nl) 2012-06-06 2013-12-09 B B A Participaties B V Bronbemalingsinrichting.
CA2779967C (fr) * 2012-06-15 2018-11-27 Hart Oilfield Rentals Ltd. Palette a patins combinee modulaire
USD682317S1 (en) 2012-06-28 2013-05-14 Don V. Carruth Plunger adapter
US9016068B2 (en) * 2012-07-13 2015-04-28 United Technologies Corporation Mid-turbine frame with oil system mounts
CN202707463U (zh) 2012-08-02 2013-01-30 兰州矿场机械有限公司 五缸柱塞泵
USD693200S1 (en) 2012-08-28 2013-11-12 Lee Valley Tools, Ltd. Bench stop
US9500195B2 (en) 2012-11-16 2016-11-22 George H Blume Integrated design fluid end suction manifold
US20140147291A1 (en) 2012-11-28 2014-05-29 Baker Hughes Incorporated Reciprocating pump assembly and method thereof
USD713101S1 (en) 2012-11-28 2014-09-09 Classic Brands, LLC Bottle for a wild bird feeder
CN203067205U (zh) 2013-01-08 2013-07-17 湖北中油科昊机械制造有限公司 一种新型煤层气固井泵
US20140196570A1 (en) * 2013-01-14 2014-07-17 Fts International Lightened Rotating Member and Method of Producing Same
USD692026S1 (en) 2013-01-23 2013-10-22 Fna Ip Holdings, Inc. Pump
US20140219824A1 (en) 2013-02-06 2014-08-07 Baker Hughes Incorporated Pump system and method thereof
US8707853B1 (en) * 2013-03-15 2014-04-29 S.P.M. Flow Control, Inc. Reciprocating pump assembly
USD704385S1 (en) 2013-04-02 2014-05-06 Mark Hoofman Portable hanging animal feeder
CA153846S (en) 2013-05-22 2014-09-05 Spm Flow Control Inc Plunger pump thru rod
US9334968B2 (en) 2013-10-10 2016-05-10 PSI Pressure Systems Corp. High pressure fluid system
CN103850908A (zh) * 2014-03-20 2014-06-11 衡阳中地装备探矿工程机械有限公司 分体掀盖式泵体结构的泥浆泵
MX2017000021A (es) 2014-06-27 2017-05-01 Spm Flow Control Inc Sistema amortiguador de tren impulsor de bomba y sistemas de control y metodo para los mismos.
EA034261B1 (ru) 2014-07-25 2020-01-22 Эс.Пи.Эм. ФЛОУ КОНТРОЛ, ИНК. Система опор для возвратно-поступательного насоса и способ сборки
US9976544B2 (en) 2014-07-31 2018-05-22 Fmc Technologies, Inc. Pump fluid end assembly mounting system
CN204162283U (zh) * 2014-08-19 2015-02-18 锐展(铜陵)科技有限公司 一种发动机缸体上线吊运装置
CN104355227B (zh) * 2014-11-17 2017-04-12 天津博瑞康机械制造有限公司 卧式螺旋沉降离心机转鼓及螺杆的吊装工具
CN104528511B (zh) * 2014-11-20 2017-04-12 上海中曼石油装备有限公司 一种泥浆泵曲轴的吊装方法
WO2016134464A1 (fr) 2015-02-25 2016-09-01 A.H.M.S., Inc. Module de mécanisme d'entraînement pour une pompe à mouvement de va-et-vient
USD759728S1 (en) * 2015-07-24 2016-06-21 S.P.M. Flow Control, Inc. Power end frame segment
US20170370480A1 (en) 2016-06-23 2017-12-28 S.P.M. Flow Control, Inc. Large bore plug valve
WO2021102036A1 (fr) 2019-11-18 2021-05-27 Kerr Machine Co. Pompe haute pression

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2056622A (en) * 1933-04-04 1936-10-06 Sulzer Ag Multicylinder reciprocating piston machine
US4477237A (en) * 1982-05-10 1984-10-16 Grable William A Fabricated reciprocating piston pump
US20080078583A1 (en) * 2006-09-28 2008-04-03 Milburn Eugene Cummins Method for assembling a modular fluid end for duplex pumps
US20100129249A1 (en) * 2007-05-17 2010-05-27 Dresser Italia S.R.L. Frame for fluid machines
EP2397694A1 (fr) * 2010-06-21 2011-12-21 Fives Cryomec AG Unité d'entraînement pour une pompe alternative

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9695812B2 (en) 2013-03-15 2017-07-04 S.P.M. Flow Control, Inc. Reciprocating pump assembly
US10316832B2 (en) 2014-06-27 2019-06-11 S.P.M. Flow Control, Inc. Pump drivetrain damper system and control systems and methods for same
US11181101B2 (en) 2014-06-27 2021-11-23 Spm Oil & Gas Inc. Pump drivetrain damper system and control systems and methods for same
US10677244B2 (en) 2014-07-25 2020-06-09 S.P.M. Flow Control, Inc. System and method for reinforcing reciprocating pump
USD791192S1 (en) 2014-07-25 2017-07-04 S.P.M. Flow Control, Inc. Power end frame segment
US9879659B2 (en) 2014-07-25 2018-01-30 S.P.M. Flow Control, Inc. Support for reciprocating pump
US11898553B2 (en) 2014-07-25 2024-02-13 Spm Oil & Gas Inc. Power end frame assembly for reciprocating pump
US10393182B2 (en) 2014-07-25 2019-08-27 S.P.M. Flow Control, Inc. Power end frame assembly for reciprocating pump
US11746775B2 (en) 2014-07-25 2023-09-05 Spm Oil & Gas Inc. Bearing system for reciprocating pump and method of assembly
US11204030B2 (en) 2014-07-25 2021-12-21 Spm Oil & Gas Inc. Support for reciprocating pump
US10087992B2 (en) 2014-07-25 2018-10-02 S.P.M. Flow Control, Inc. Bearing system for reciprocating pump and method of assembly
US10520037B2 (en) 2014-07-25 2019-12-31 S.P.M. Flow Control, Inc. Support for reciprocating pump
US11421682B2 (en) 2014-12-22 2022-08-23 Spm Oil & Gas Inc. Reciprocating pump with dual circuit power end lubrication system
US10352321B2 (en) 2014-12-22 2019-07-16 S.P.M. Flow Control, Inc. Reciprocating pump with dual circuit power end lubrication system
USD791193S1 (en) 2015-07-24 2017-07-04 S.P.M. Flow Control, Inc. Power end frame segment
USD870157S1 (en) 2015-07-24 2019-12-17 S.P.M. Flow Control, Inc. Power end frame segment
USD870156S1 (en) 2015-07-24 2019-12-17 S.P.M. Flow Control, Inc. Power end frame segment
US10436766B1 (en) 2015-10-12 2019-10-08 S.P.M. Flow Control, Inc. Monitoring lubricant in hydraulic fracturing pump system

Also Published As

Publication number Publication date
US10393182B2 (en) 2019-08-27
EA201790256A1 (ru) 2017-07-31
AU2015292354B2 (en) 2018-12-13
MX2017000888A (es) 2017-05-04
CA3042764A1 (fr) 2016-01-28
EA201790257A1 (ru) 2017-06-30
CA3031128A1 (fr) 2016-01-28
EP3194778B1 (fr) 2020-12-23
MX2022005559A (es) 2022-06-09
CN106715907A (zh) 2017-05-24
CN106937530A (zh) 2017-07-07
USD791192S1 (en) 2017-07-04
EP3172443A1 (fr) 2017-05-31
CA2955818C (fr) 2019-03-12
MX2017000969A (es) 2017-04-27
EP3172443A4 (fr) 2018-02-21
CA2955829C (fr) 2021-03-02
MX2022004208A (es) 2022-07-19
AU2015292354A1 (en) 2017-02-02
WO2016015012A1 (fr) 2016-01-28
CA2955673A1 (fr) 2016-01-28
AU2019201317B2 (en) 2021-04-08
MX2017000971A (es) 2017-04-27
EP3660311A3 (fr) 2020-07-29
WO2016014988A1 (fr) 2016-01-28
MX2017000887A (es) 2017-05-04
AU2015292399A1 (en) 2017-02-02
US11204030B2 (en) 2021-12-21
US10520037B2 (en) 2019-12-31
WO2016014967A8 (fr) 2017-03-02
US10677244B2 (en) 2020-06-09
CN106937530B (zh) 2019-11-05
EP3194778A4 (fr) 2018-01-24
EP3194777A4 (fr) 2018-02-21
CA2955814C (fr) 2019-06-25
CN111502943A (zh) 2020-08-07
EA034261B1 (ru) 2020-01-22
WO2016015012A8 (fr) 2017-03-02
CA2955818A1 (fr) 2016-01-28
EA201790255A1 (ru) 2017-05-31
CA3031128C (fr) 2020-10-27
BR112017001344A2 (pt) 2017-11-14
CN111502943B (zh) 2023-04-07
BR112017001348A2 (pt) 2017-11-14
US20160025090A1 (en) 2016-01-28
CN106687688B (zh) 2019-12-24
EP3172436A4 (fr) 2018-03-07
BR112017001351A2 (pt) 2017-11-14
AU2015292348B2 (en) 2018-12-06
CA3042764C (fr) 2021-11-02
EA033262B1 (ru) 2019-09-30
US20160025089A1 (en) 2016-01-28
US9879659B2 (en) 2018-01-30
US20180163709A1 (en) 2018-06-14
CA2955829A1 (fr) 2016-01-28
CN106687688A (zh) 2017-05-17
BR112017001328A2 (pt) 2018-03-27
US20160025088A1 (en) 2016-01-28
CN107076139B (zh) 2020-04-17
US10087992B2 (en) 2018-10-02
CA2955814A1 (fr) 2016-01-28
US11746775B2 (en) 2023-09-05
AU2019201317A1 (en) 2019-03-14
US11898553B2 (en) 2024-02-13
CA2955673C (fr) 2020-08-04
US20160025082A1 (en) 2016-01-28
US20200141401A1 (en) 2020-05-07
US20190032720A1 (en) 2019-01-31
AU2015292330A1 (en) 2017-02-02
EP3172436A1 (fr) 2017-05-31
AU2015292330B2 (en) 2018-12-13
WO2016015006A1 (fr) 2016-01-28
EP3660311A2 (fr) 2020-06-03
CN107076139A (zh) 2017-08-18
EA033624B1 (ru) 2019-11-11
EA201790258A1 (ru) 2017-06-30
EA033104B1 (ru) 2019-08-30
US20190277341A1 (en) 2019-09-12
EP3194777A1 (fr) 2017-07-26
EP3194778A1 (fr) 2017-07-26
AU2015292348A1 (en) 2017-02-02
CN110360074A (zh) 2019-10-22
AU2015292399B2 (en) 2018-12-06

Similar Documents

Publication Publication Date Title
AU2019201317B2 (en) Support for reciprocating pump
US11480170B2 (en) Support for reciprocating pump

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 15824524

Country of ref document: EP

Kind code of ref document: A1

DPE1 Request for preliminary examination filed after expiration of 19th month from priority date (pct application filed from 20040101)
ENP Entry into the national phase

Ref document number: 2955814

Country of ref document: CA

WWE Wipo information: entry into national phase

Ref document number: MX/A/2017/000887

Country of ref document: MX

NENP Non-entry into the national phase

Ref country code: DE

ENP Entry into the national phase

Ref document number: 2015292399

Country of ref document: AU

Date of ref document: 20150724

Kind code of ref document: A

REEP Request for entry into the european phase

Ref document number: 2015824524

Country of ref document: EP

REG Reference to national code

Ref country code: BR

Ref legal event code: B01A

Ref document number: 112017001328

Country of ref document: BR

WWE Wipo information: entry into national phase

Ref document number: 2015824524

Country of ref document: EP

WWE Wipo information: entry into national phase

Ref document number: 201790255

Country of ref document: EA

REG Reference to national code

Ref country code: BR

Ref legal event code: B01E

Ref document number: 112017001328

Country of ref document: BR

ENP Entry into the national phase

Ref document number: 112017001328

Country of ref document: BR

Kind code of ref document: A2

Effective date: 20170123